JPH01190920A - Twin turbo type internal combustion engine - Google Patents
Twin turbo type internal combustion engineInfo
- Publication number
- JPH01190920A JPH01190920A JP63014015A JP1401588A JPH01190920A JP H01190920 A JPH01190920 A JP H01190920A JP 63014015 A JP63014015 A JP 63014015A JP 1401588 A JP1401588 A JP 1401588A JP H01190920 A JPH01190920 A JP H01190920A
- Authority
- JP
- Japan
- Prior art keywords
- exhaust
- pressure stage
- communication pipe
- exhaust passage
- switching valve
- 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
- 238000002485 combustion reaction Methods 0.000 title claims description 10
- 238000005192 partition Methods 0.000 claims description 9
- 238000000638 solvent extraction Methods 0.000 abstract 3
- 239000007789 gas Substances 0.000 description 36
- 230000000694 effects Effects 0.000 description 4
- 230000007246 mechanism Effects 0.000 description 4
- 230000008602 contraction Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000011144 upstream manufacturing Methods 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 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
- F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
- F02B37/007—Engines characterised by provision of pumps driven at least for part of the time by exhaust with exhaust-driven pumps arranged in parallel, e.g. at least one pump supplying alternatively
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
- F01N13/00—Exhaust or silencing apparatus characterised by constructional features ; Exhaust or silencing apparatus, or parts thereof, having pertinent characteristics not provided for in, or of interest apart from, groups F01N1/00 - F01N5/00, F01N9/00, F01N11/00
- F01N13/08—Other arrangements or adaptations of exhaust conduits
- F01N13/10—Other arrangements or adaptations of exhaust conduits of exhaust manifolds
- F01N13/107—More than one exhaust manifold or exhaust collector
-
- 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
- F02B37/013—Engines characterised by provision of pumps driven at least for part of the time by exhaust with exhaust-driven pumps arranged in series
-
- 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
- F02B37/02—Gas passages between engine outlet and pump drive, e.g. reservoirs
- F02B37/025—Multiple scrolls or multiple gas passages guiding the gas to the pump drive
-
- 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
- F02B29/00—Engines characterised by provision for charging or scavenging not provided for in groups F02B25/00, F02B27/00 or F02B33/00 - F02B39/00; Details thereof
- F02B29/04—Cooling of air intake supply
- F02B29/0406—Layout of the intake air cooling or coolant circuit
- F02B29/0412—Multiple heat exchangers arranged in parallel or in series
-
- 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】
（産業上の利用分野）
本発明は、複数気筒を２群に分割し、それぞれの気筒群
に排気ターボ過給機を備えたツインターボ式内燃機関に
関するものである。DETAILED DESCRIPTION OF THE INVENTION (Field of Industrial Application) The present invention relates to a twin-turbo internal combustion engine in which a plurality of cylinders are divided into two groups and each cylinder group is provided with an exhaust turbo supercharger.
（従来技術及びその問題点）
この種のツインターボ式内燃機関では、従来から２本の
排気通路の途中を連絡管で連通ずるようにした先行技術
が実開昭６０−１７８３２９号で知られている。(Prior art and its problems) In this type of twin-turbo internal combustion engine, a prior art in which two exhaust passages are connected through a connecting pipe is known from Utility Model Application No. 178329/1983. There is.
しかしながら、この先行技術では２本の排気通路を流れ
る排気ガスの脈動パルスが相互に干渉し合い、脈動パル
スが低下して過給効率の面で改善の余地がある。また、
特に低速時には排気ガス量が少なく過給効率の低下が著
しい。However, in this prior art, the pulsating pulses of the exhaust gas flowing through the two exhaust passages interfere with each other, reducing the pulsating pulses and leaving room for improvement in terms of supercharging efficiency. Also,
Particularly at low speeds, the amount of exhaust gas is small and the supercharging efficiency is significantly reduced.
複数気筒を２群に分割して排気ターボ過給機へ排気を流
す技術が特公昭３ｇ−１１５４号、特公昭５９−６９２
号に開示しである。The technology of dividing multiple cylinders into two groups and sending exhaust gas to an exhaust turbo supercharger was published in Tokoku Sho 3g-1154 and Sho 59-692.
This is disclosed in the issue.
（発明の目的）
本発明は、第１にツインターボ式内燃機関において、排
気干渉による過給効率の低下を防止でき、且つ中低速域
での性能を低圧段排気ターボ過給機で向上できるツイン
ターボ式内燃機関を提供することを目的としている。(Purpose of the Invention) The present invention firstly provides a twin-turbo internal combustion engine that can prevent a decrease in supercharging efficiency due to exhaust interference and improve performance in the medium and low speed range with a low-pressure stage exhaust turbo supercharger. The purpose is to provide a turbo-type internal combustion engine.
（発明の構成）
（１）技術的手段
本発明は、複数気筒を２群に分割し、それぞれの気筒群
に排気ターボ過給機を備えたツインターボ式内燃機関に
おいて、各気筒群毎に高圧段排気ターボ過給機を設け、
各高圧段排気ターボ過給機と各気筒群とを繋ぐ２本の排
気通路の間に両排気通路を連通ずる連絡管を設け、一方
の排気ターボ過給機にツインスクロールタービンを設け
、このツインスクロールタービンに繋がる第１排気通路
の前記連絡管より下流側に第１排気通路の断面積を２分
割する隔壁を形成し、前記第１排気通路と連絡管との接
続部に閉弁時には連絡管開口を閉塞し、開弁時には連絡
管を第１排気通路の一方の分割通路に連通ずるように切
換える第１切換弁を設け、他方のターボ過給機に繋がる
第２排気通路と連絡管の接続部に、閉弁時には連絡管開
口を閉塞し、開弁時には第２排気通路の排気ガスの全量
を連絡管へ導くように切換える第２切換弁を設け、前記
両高圧段排気ターボ過給機の下流側にツインスクロール
タービンを有する低圧段排気ターボ過給機を１基設け、
低圧段排気ターボ過給機のツインスクロールタービンの
各渦巻き室へ前記高圧段排気ターボ過給機からの排気ガ
スを独立して導く排気接続管を設け、低圧段排気ターボ
過給機からの過給給気を両高圧段排気ターボ過給機へ導
く給気接続管を設けたことを特徴とするツインターボ式
内燃機関である。(Structure of the Invention) (1) Technical Means The present invention provides a twin-turbo internal combustion engine in which a plurality of cylinders are divided into two groups and each cylinder group is equipped with an exhaust turbo supercharger. A stage exhaust turbo supercharger is installed,
A communication pipe is provided between the two exhaust passages connecting each high-pressure stage exhaust turbo supercharger and each cylinder group, and a twin scroll turbine is installed in one of the exhaust turbo superchargers. A partition wall that divides the cross-sectional area of the first exhaust passage into two is formed on the downstream side of the communication pipe of the first exhaust passage connected to the scroll turbine, and a communication pipe is formed at the connection between the first exhaust passage and the communication pipe when the valve is closed. A first switching valve is provided that closes the opening and switches the connecting pipe to communicate with one of the divided passages of the first exhaust passage when the valve is opened, and connects the connecting pipe to the second exhaust passage that connects to the other turbocharger. A second switching valve is provided in the section so as to close the connecting pipe opening when the valve is closed, and to conduct the entire amount of exhaust gas in the second exhaust passage to the connecting pipe when the valve is opened, so that the two high-pressure stage exhaust turbo superchargers One low-pressure stage exhaust turbo supercharger with a twin scroll turbine is installed on the downstream side,
An exhaust connection pipe is provided to independently guide the exhaust gas from the high pressure stage exhaust turbo supercharger to each spiral chamber of the twin scroll turbine of the low pressure stage exhaust turbo supercharger, and supercharging from the low pressure stage exhaust turbo supercharger is provided. This is a twin-turbo internal combustion engine characterized by the provision of an air intake connection pipe that guides air intake to both high-pressure stage exhaust turbo superchargers.
（２）作用
両切換弁の開弁時には、隔壁およびツインスクロールタ
ービンで排気干渉を防止しながら排気ガスを高圧段排気
ターボ過給機のツインスクロールタービンへ流し、高効
率で過給する。(2) Effect When both switching valves are opened, exhaust gas is flowed to the twin scroll turbine of the high pressure stage exhaust turbo supercharger while preventing exhaust interference with the partition wall and the twin scroll turbine, and is supercharged with high efficiency.
同時に、排気接続管の一方から低圧段排気ターボ過給機
のツインスクロールタービンへ排気ガスを流し、更に過
給する。At the same time, exhaust gas flows from one side of the exhaust connection pipe to the twin scroll turbine of the low-pressure stage exhaust turbo supercharger for further supercharging.
両切換弁の閉弁時には、両排気通路と連絡管とを遮断し
て連絡管の影響を無くし、高圧段排気ターボ過給機の過
給効率を向上し、排気接続管から低圧段排気ターボ過給
機に独立して排気ガスを流し、低圧段排気ターボ過給機
の過給効率を向上する。When both switching valves are closed, both exhaust passages and the communication pipe are shut off to eliminate the influence of the communication pipe, improving the supercharging efficiency of the high-pressure stage exhaust turbocharger, and connecting the low-pressure stage exhaust turbosupercharger from the exhaust connection pipe. Flows exhaust gas independently to the charger to improve the supercharging efficiency of the low-pressure stage exhaust turbo supercharger.
（実施例）
本発明を採用したツインターボ式ディーゼル機関を示す
第１図で、１０は機関本体である。この機関本体１０は
６気筒のシリンダ１１を有しており、シリンダ１１の排
気マニホールド１２は３気筒分ずつ集合して第１排気通
路１３と第２排気通路１４に繋がっている。(Example) In FIG. 1 showing a twin-turbo diesel engine employing the present invention, 10 is an engine body. This engine main body 10 has six cylinders 11, and the exhaust manifolds 12 of the cylinders 11 are connected to a first exhaust passage 13 and a second exhaust passage 14 in groups for three cylinders each.
第１排気通路１３は高圧段排気ターボ過給機１５に接続
し、高圧段排気ターボ過給機１５はツインスクロールタ
ービン１６に２室の渦巻き室を有している。第２排気通
路１４は高圧段排気ターボ過給機１７に接続し、高圧段
排気ターボ過給機１７はシングルスクロールタービン１
８に単一の渦巻き室を有している。高圧段排気ターボ過
給機１５．１７のブロワ１９．２０は給気管２１．２２
で機関本体１０の給気マニホールド２３に連通し、給気
マニホールド２３にはインタークーラ２４が設けられて
いる。給気管２１には逆止弁２５を介装しである。なお
、図中２７はインタークーラである。The first exhaust passage 13 is connected to a high pressure stage exhaust turbo supercharger 15, and the high pressure stage exhaust turbo supercharger 15 has a twin scroll turbine 16 and two spiral chambers. The second exhaust passage 14 is connected to a high pressure stage exhaust turbo supercharger 17, and the high pressure stage exhaust turbo supercharger 17 is connected to the single scroll turbine 1.
8 has a single volute chamber. The blower 19.20 of the high pressure stage exhaust turbo supercharger 15.17 is connected to the air supply pipe 21.22.
The intercooler 24 is connected to the air supply manifold 23 of the engine main body 10, and the air supply manifold 23 is provided with an intercooler 24. A check valve 25 is interposed in the air supply pipe 21. Note that 27 in the figure is an intercooler.
更に、両高圧段排気ターボ過給機１５．１７の下流側に
は詳しくは後述する低圧段排気ターボ過給機２６を１基
だけ設けである。Furthermore, only one low pressure stage exhaust turbo supercharger 26, which will be described in detail later, is provided downstream of both high pressure stage exhaust turbo superchargers 15 and 17.
前記第１排気通路１３と第２排気通路１４の間には連絡
管３０を架設してあり、連絡管３０で第１排気通路１３
と第２排気通路１４を連通している。連絡管３０の両端
と第１排気通路１３、第２排気通路１４との接続部には
、第１切換弁３１、第２切換弁３２が設けられており、
第１切換弁３１・第２切換弁３２で連絡管３０を詳しく
は後述するように開閉制御する機能を果たしている。連
絡管３０の中央部には伸縮継手３３が設けられている。A communication pipe 30 is installed between the first exhaust passage 13 and the second exhaust passage 14, and the communication pipe 30 connects the first exhaust passage 13 to the first exhaust passage 13.
and communicates with the second exhaust passage 14. A first switching valve 31 and a second switching valve 32 are provided at the connection parts between both ends of the communication pipe 30 and the first exhaust passage 13 and the second exhaust passage 14.
The first switching valve 31 and the second switching valve 32 function to control opening and closing of the communication pipe 30 as will be described in detail later. An expansion joint 33 is provided in the center of the communication pipe 30.
前記第１排気通路１３の連絡管３０より下流側には隔壁
３４が形成されており、隔壁３４で第１排気通路１３の
断面積を略２等分するように分割している。したがって
、第１排気通路１３を流れる排気ガスは隔壁３４で区画
された分割通路３５．３６を通ってツインスクロールタ
ービン１６の渦巻き室にそれぞれ独立して流れ込むよう
になっている。A partition wall 34 is formed on the downstream side of the communication pipe 30 of the first exhaust passage 13, and the partition wall 34 divides the cross-sectional area of the first exhaust passage 13 into approximately two equal parts. Therefore, the exhaust gas flowing through the first exhaust passage 13 passes through the divided passages 35 and 36 divided by the partition wall 34 and flows into the spiral chamber of the twin scroll turbine 16 independently.
第１切換弁３１は支点３７で軸支されており、支点３７
は連絡管３０の開口の上流側近傍位置に配置しである。The first switching valve 31 is pivoted on a fulcrum 37, and the fulcrum 37
is arranged near the upstream side of the opening of the communication pipe 30.
また、第２切換弁３２の支点３８は連絡管３０の開口の
下流側近傍位置に配置しである。Further, the fulcrum 38 of the second switching valve 32 is arranged near the downstream side of the opening of the communication pipe 30.
前記第１切換弁３１、第２切換弁３２は第１図で図示す
る中低速、高負荷時には、第１切換弁３１の先端部が隔
壁３４に一致するように半開状態で開弁じ、第２切換弁
３２は第２排気通路１４の排気ガスの全量を連絡管３０
へ流すように全開状態で開弁じている。次に、高速、高
負荷時には第２図に示すように連絡管３０の両端開口を
閉塞するように閉弁している。The first switching valve 31 and the second switching valve 32 are opened in a half-open state so that the tip of the first switching valve 31 coincides with the partition wall 34, and the second switching valve 32 is opened at medium-low speed and high load as shown in FIG. The switching valve 32 transfers the entire amount of exhaust gas from the second exhaust passage 14 to the communication pipe 30.
The valve is fully open so that water flows to the tank. Next, at high speeds and high loads, the valves are closed to block both ends of the communication pipe 30, as shown in FIG.
前記ツインスクロールタービン１６とシングルスクロー
ルタービン１８と低圧段排気ターボ過給機２６のツイン
スクロールタービン６０との間は、ツインスクロールタ
ービン６０の各渦巻き室へ排気ガスを流す排気接続管６
１．６２で接続しである。排気接続管６１．６２の基端
部には自在継手６３．６４が介装しである。排気接続管
６１．６２の先端部は、タービン支え６５で機関本体１
０を搭載する基台に支持しである。更に、排気接続管６
１．６２の先端部は前記ツインスクロールタービン６０
に連結し、両タービン１６．１８からの排気ガスを各々
独立してツインスクロールタービン６０内の各渦巻き室
へ導くようになっている。Between the twin scroll turbine 16, the single scroll turbine 18, and the twin scroll turbine 60 of the low-pressure stage exhaust turbo supercharger 26, there is an exhaust connecting pipe 6 that allows exhaust gas to flow into each spiral chamber of the twin scroll turbine 60.
It is connected at 1.62. Universal joints 63, 64 are interposed at the proximal ends of the exhaust connection pipes 61, 62. The tips of the exhaust connection pipes 61 and 62 are connected to the engine body 1 by the turbine support 65.
It is supported by a base on which 0 is mounted. Furthermore, the exhaust connection pipe 6
The tip of 1.62 is the twin scroll turbine 60.
The exhaust gases from both turbines 16 and 18 are each independently guided to each spiral chamber in the twin scroll turbine 60.
低圧段排気ターボ過給機２６のブロワ７０には給気接続
管７１が接続し、給気接続管７１はインジェクタークー
ラー７２を介して高圧側のブロア１９．２０に繋がって
いる。An air supply connection pipe 71 is connected to the blower 70 of the low pressure stage exhaust turbo supercharger 26, and the air supply connection pipe 71 is connected to the high pressure side blower 19.20 via an injector cooler 72.
以上の構成では、第１排気通路１３、第２排気通路１４
の排気ガス量が減って高圧段排気ターボ過給機１５．１
７の過給効率が低下する場合に、第１図のように第１切
換弁３１、第２切換弁３２を切換えて、第１排気通路１
３を流れる排気ガスを第１切換弁３１で分割通路３５に
案内し、第２排気通路１４を流れる排気ガスを第２切換
弁３２で連絡管３０に通し、連絡管３０から第１切換弁
３１で分割通路３６に案内する。In the above configuration, the first exhaust passage 13, the second exhaust passage 14
The amount of exhaust gas is reduced and the high pressure stage exhaust turbo supercharger 15.1
7, the first switching valve 31 and the second switching valve 32 are switched as shown in FIG.
3 is guided to the divided passage 35 by the first switching valve 31, exhaust gas flowing through the second exhaust passage 14 is guided to the communication pipe 30 by the second switching valve 32, and from the communication pipe 30 to the first switching valve 31. guide to the divided passage 36.
したがって、２群に分割したシリンダ１１の排気ガスを
ツインスクロールタービン１６の渦巻き室に分割して供
給し、高圧段排気ターボ過給機１５に対しては相対的に
排気ガス量が増えることになり、所謂可変人口ノズル（
ＶＧＳ）と同様の働きをして、少ない排気ガス量でも高
圧段排気ターボ過給機１５は高い過給効率を発揮する。Therefore, the exhaust gas of the cylinders 11 divided into two groups is divided and supplied to the spiral chamber of the twin scroll turbine 16, and the amount of exhaust gas relative to the high pressure stage exhaust turbo supercharger 15 increases. , so-called variable population nozzle (
VGS), the high-pressure stage exhaust turbo supercharger 15 exhibits high supercharging efficiency even with a small amount of exhaust gas.
また、２群に分割したシリンダ１１の排気ガスを隔壁３
４でツインスクロールタービン１６の渦巻き室にそれぞ
れ独立した状態で供給し、分割通路３５．３６を流れる
排気ガスの脈動パルスが相互に干渉せず、高い脈動パル
スで高圧段排気ターボ過給機１５の過給効果を上げる。In addition, the exhaust gas from the cylinders 11 divided into two groups is transferred to the partition wall 3.
The pulsating pulses of exhaust gas flowing through the divided passages 35 and 36 do not interfere with each other, and the high-pressure stage exhaust turbo supercharger 15 is supplied with high pulsating pulses. Increase supercharging effect.
更に、タービン１６から排気接続管６１を通って低圧段
排気ターボ過給機２６のツインスクロールタービン６０
へ供給された排気ガスは、断面積が小さ−な排気接続管
６１からツインスクロールタービン６０の渦巻き室の一
方へ流れ込むことになる。したがって、低圧段排気ター
ボ過給機２６１；対して相対的に排気ガス量が増えるこ
とになり、前述と同様に低圧段排気ターボ過給機２６を
高効率で駆動し、ブロワ７０から過給給気が給気接続管
７１を通ってブロワ１９．２０に流れ込む。Further, the twin scroll turbine 60 of the low pressure stage exhaust turbo supercharger 26 is connected from the turbine 16 through the exhaust connection pipe 61.
The exhaust gas supplied to the twin scroll turbine 60 flows into one of the spiral chambers of the twin scroll turbine 60 through the exhaust connecting pipe 61 having a small cross-sectional area. Therefore, the amount of exhaust gas increases relative to the low pressure stage exhaust turbo supercharger 261; therefore, the low pressure stage exhaust turbo supercharger 26 is driven with high efficiency as described above, and supercharging is supplied from the blower 70. Air flows through the air supply connection 71 into the blower 19.20.
この第１図の運転状態では、回転数ｎに対する出力Ｐの
グラフである第３図において、Ｒ１の範囲で特性Ｘ１を
発揮する。この特性Ｘ１は、高圧段排気ターボ過給機１
５．１７だけを作動した場合の特性ｘ２、領域Ｗ２と比
較して、高圧段排気ターボ過給機１５側のみの作動によ
って領域Ｗ１分だけ中低速域の出力Ｐが向上する。In the operating state shown in FIG. 1, the characteristic X1 is exhibited in the range R1 in FIG. 3, which is a graph of the output P versus the rotational speed n. This characteristic X1 is the high pressure stage exhaust turbo supercharger 1
Compared to characteristic x2 and region W2 when only 5.17 is operated, the output P in the medium and low speed range is improved by region W1 by operating only the high pressure stage exhaust turbo supercharger 15 side.
第２図の高速、高負荷時には第１切換弁３１、第２切換
弁３２が連絡管３０の両端開口を閉塞するように閉弁し
、連絡管３０は第１排気通路１３、第２排気通路１４か
ら完全に遮断され、第１排気通路１３、第２排気通路１
４の排気ガスは直接に高圧段排気ターボ過給機１５．１
７へ流れる。At high speeds and high loads as shown in FIG. 2, the first switching valve 31 and the second switching valve 32 are closed so as to close the openings at both ends of the connecting pipe 30, and the connecting pipe 30 is connected to the first exhaust passage 13 and the second exhaust passage. 14, the first exhaust passage 13 and the second exhaust passage 1
4 exhaust gas is directly sent to the high pressure stage exhaust turbo supercharger 15.1
Flows to 7.
この高速、高負荷時には第１排気通路１３、第２排気通
路１４の排気ガス量が十分に増えているので、高圧段排
気ターボ過給機１５．１７は高い過給効率を発揮する。At this high speed and high load, the amount of exhaust gas in the first exhaust passage 13 and second exhaust passage 14 increases sufficiently, so the high pressure stage exhaust turbo supercharger 15, 17 exhibits high supercharging efficiency.
また、連絡管３０は第１切換弁３１、第２切換弁３２で
遮断されているので、連絡管３０の容積が第１排気通路
１３、第２排気通路１４を流れる排気ガスの脈動パルス
を減衰することも無く、この面でも過給効率が向上する
。Furthermore, since the communication pipe 30 is blocked by the first switching valve 31 and the second switching valve 32, the volume of the communication pipe 30 attenuates the pulsating pulse of the exhaust gas flowing through the first exhaust passage 13 and the second exhaust passage 14. This also improves supercharging efficiency.
更に、下流側に設けられた低圧段排気ターボ過給機２６
のツインスクロールタービン６０に排気接続管６１．６
２を通って、各渦巻き室へ独立して両タービン１６．１
８から排気ガスが流れ込み、両タービン１６．１８双方
からの排気ガスが排気干渉を起こさず、低圧段排気ター
ボ過給機２６の過給効率が高い。Furthermore, a low pressure stage exhaust turbo supercharger 26 provided on the downstream side
Exhaust connection pipe 61.6 to twin scroll turbine 60 of
2 to both turbines 16.1 independently to each volute chamber.
8, the exhaust gases from both turbines 16 and 18 do not cause exhaust interference, and the supercharging efficiency of the low-pressure stage exhaust turbo supercharger 26 is high.
第２図の運転状態は第３図の領域Ｗ３の範囲（回転数Ｒ
２）で実行し、特性Ｘ３を発揮する。The operating state in Figure 2 is within the range W3 (rotational speed R) in Figure 3.
2) and exhibits characteristic X3.
次に、第４図で第１切換弁３１、第２切換弁３２の切換
機構を説明する。第４図中で、第１切換弁３１、第２切
換弁３２の基端部にはアーム４０．４１を第１切換弁３
１、第２切換弁３２に連続して一体に支点３７．３８回
りに回動自在に形成しである。アーム４０．４１は第１
排気通路１３、第２排気通路１４の外方に突出している
。Next, the switching mechanism of the first switching valve 31 and the second switching valve 32 will be explained with reference to FIG. In FIG. 4, an arm 40.41 is attached to the base end of the first switching valve 31 and the second switching valve 32.
1. It is formed continuously and integrally with the second switching valve 32 so as to be rotatable around fulcrums 37 and 38. Arm 40.41 is the first
It protrudes outward from the exhaust passage 13 and the second exhaust passage 14.
アーム４０．４１の先端部にはリンク４２がピン４３．
４４で回動自在に連結しており、リンク４２で第１切換
弁３１、第２切換弁３２の開閉動作を連動するようにな
っている。アーム４０の中間部には、エアシリンダ４５
（アクチュエーター）のロッド４６が回動自在に連結し
ており、ロッド４６の伸縮ストロークで第１切換弁３１
、第２切換弁３２を開閉する機能を発揮する。エアシリ
ンダ４５は比較的小型で、１個だけ設けられている。A link 42 is attached to a pin 43. at the tip of the arm 40.41.
The opening and closing operations of the first switching valve 31 and the second switching valve 32 are linked by a link 42. An air cylinder 45 is installed in the middle of the arm 40.
A rod 46 (actuator) is rotatably connected, and the expansion and contraction stroke of the rod 46 causes the first switching valve 31 to
, functions to open and close the second switching valve 32. The air cylinder 45 is relatively small, and only one air cylinder is provided.
第４図の状態ではエアシリンダ４５のロッド４６は最も
短縮した位置にある。また、アーム４０．４１の長さは
、この状態からストロークＳだけ伸びて最も伸長した位
置で、第１切換弁３１をθｌ″だけ回動し、同時に第２
切換弁３２をθ２だけ回動して、第１切換弁３１、第２
切換弁３２を同時に閉弁し得るようにＬＬ：Ｌ２の比を
設定しである。In the state shown in FIG. 4, the rod 46 of the air cylinder 45 is at its shortest position. Further, the length of the arm 40.41 is extended from this state by a stroke S, and at the most extended position, the first switching valve 31 is rotated by θl'', and at the same time the second
By rotating the switching valve 32 by θ2, the first switching valve 31 and the second switching valve 32 are rotated by θ2.
The ratio of LL:L2 is set so that the switching valves 32 can be closed at the same time.
なお、エアシリンダ４５の代わりに真空ポンプまたはス
テップモータ等の他のアクチュエーターを使用すること
もでき、リンク４２、アーム４０の途中に任意の長さで
固定可能な長さ調整機構４８．４９を設けることも可能
である。Note that other actuators such as a vacuum pump or a step motor may be used instead of the air cylinder 45, and length adjustment mechanisms 48 and 49 are provided in the middle of the link 42 and the arm 40, which can be fixed at any length. It is also possible.
エアシリンダ４５には配管４７．４７ａを通って圧縮空
気供給機構５０からの圧縮空気が流通しており、圧縮空
気供給機構５０は制御装置５１で制御される。更に制御
装置５１には機関本体１０（第１図）の回転計（図示せ
ず）からの回転数信号５３や第１排気通路１３、第２排
気通路１４の圧力計５４からの圧力信号５５が入力して
おり、制御装置５１は両信号５３．５５に基づいて機関
の運転状態を半１別し、中低速、高負荷時には第１図の
ように第１切換弁３１、第２切換弁３２を開弁じ、高速
、高負荷時には第１切換弁３１、第２切換弁３２を閉弁
するようになっている。Compressed air from a compressed air supply mechanism 50 flows through the air cylinder 45 through a pipe 47.47a, and the compressed air supply mechanism 50 is controlled by a control device 51. Furthermore, the control device 51 receives a rotational speed signal 53 from a tachometer (not shown) in the engine body 10 (FIG. 1) and a pressure signal 55 from pressure gauges 54 in the first exhaust passage 13 and second exhaust passage 14. The control device 51 divides the operating state of the engine into half based on both signals 53 and 55, and at medium to low speeds and high loads, the first switching valve 31 and the second switching valve 32 are switched on as shown in FIG. The valve is opened, and the first switching valve 31 and the second switching valve 32 are closed at high speed and high load.
以上の構成では、第１切換弁３１、第２切換弁３２をリ
ンク４２で連結してエアシリンダ４５を設けたので、２
箇所の第１切換弁３１、第２切換弁３２は１個のエアシ
リンダ４５だけで開閉動作する。In the above configuration, the air cylinder 45 is provided by connecting the first switching valve 31 and the second switching valve 32 with the link 42.
The first switching valve 31 and the second switching valve 32 at the locations are opened and closed by only one air cylinder 45.
また、第１切換弁３１、第２切換弁３２はリンク４２で
連結し、第１切換弁３１が開弁している時には第２切換
弁３２も開弁し、第１切換弁３１が閉弁している時には
第２切換弁３２も閉弁する。Further, the first switching valve 31 and the second switching valve 32 are connected by a link 42, and when the first switching valve 31 is open, the second switching valve 32 is also opened, and the first switching valve 31 is closed. When this is the case, the second switching valve 32 is also closed.
したがって、第２切換弁３２が開弁している時に第１切
換弁３１が閉弁して第２排気通路１４の排気ガスの流通
が阻害されることが無く、第２排気通路１４の排気ガス
流通に抵抗が発生しない。Therefore, when the second switching valve 32 is open, the first switching valve 31 is not closed and the flow of exhaust gas in the second exhaust passage 14 is not obstructed, and the exhaust gas in the second exhaust passage 14 is not obstructed. No resistance occurs in distribution.
（発明の効果）
以上説明したように本発明によるツインターボ式内燃機
関では、両高圧段排気ターボ過給機１５゜１７の下流側
にツインスクロールタービン６０を有する低圧段排気タ
ーボ過給機２６を１基設け、低圧段排気ターボ過給機２
６のツインスクロールタービン６０の各渦巻き室へ前記
高圧段排気ターボ過給機１５．１７からの排気ガスを独
立して導く排気接続管６１．６２を設け、低圧段排気タ
ーボ過給機２６からの過給給気を両高圧段排気ターボ過
給機１５．１７へ導く給気接続管７１を設けたので、次
の効果を奏する。(Effects of the Invention) As explained above, in the twin-turbo internal combustion engine according to the present invention, the low pressure stage exhaust turbo supercharger 26 which has the twin scroll turbine 60 on the downstream side of both the high pressure stage exhaust turbo superchargers 15 and 17 is installed. 1 unit installed, 2 low pressure stage exhaust turbo superchargers
Exhaust connection pipes 61 and 62 are provided to independently guide the exhaust gas from the high pressure stage exhaust turbo supercharger 15 and 17 to each spiral chamber of the twin scroll turbine 60, and the exhaust gas from the low pressure stage exhaust turbo supercharger 26 is Since the air supply connecting pipe 71 is provided to guide the supercharged air to both the high pressure stage exhaust turbo superchargers 15 and 17, the following effects are achieved.
排気ガス量が少ない中低速時に、高圧段排気ターボ過給
機１５から低圧段排気ターボ過給機２６へ供給される排
気ガスの運動エネルギを回収して、低圧段排気ターボ過
給機２６のブロワ７０からブロワ１９へ過給給気を還流
でき、第３図のＲ１の範囲で領域Ｗ１分だけ従来より出
力Ｐが向上した特性Ｘｔを発揮できる。At medium and low speeds when the amount of exhaust gas is small, the kinetic energy of the exhaust gas supplied from the high pressure stage exhaust turbo supercharger 15 to the low pressure stage exhaust turbo supercharger 26 is recovered, and the blower of the low pressure stage exhaust turbo supercharger 26 is The supercharging air can be recirculated from 70 to the blower 19, and a characteristic Xt can be exhibited in which the output P is improved by an area W1 in the range R1 in FIG. 3 compared to the conventional one.
特に、ツインスクロールター（ン６０に排気接続管６１
だけから排気ガスを流すので、排気ガス量が少ない中低
速時にも低圧段排気ターボ過給機２６の過給効率を上げ
ることができる。In particular, the exhaust connection pipe 61 is connected to the twin scroll turbine 60.
Since the exhaust gas flows only from the exhaust gas, the supercharging efficiency of the low pressure stage exhaust turbo supercharger 26 can be increased even at medium and low speeds when the amount of exhaust gas is small.
低圧段排気ターボ過給機２６のツインスクロールタービ
ン６０には２木の排気接続管６１．６２から独立して排
気ガスを流すようにしたので、排気接続管６１．６２を
流れる排気ガスが排気干渉を起こさず、第３図のＲ２の
範囲でも過給効率が高い。Since the exhaust gas is made to flow independently from the two exhaust connection pipes 61 and 62 to the twin scroll turbine 60 of the low pressure stage exhaust turbo supercharger 26, the exhaust gas flowing through the exhaust connection pipes 61 and 62 does not interfere with the exhaust. The supercharging efficiency is high even in the range of R2 shown in FIG. 3.
Claims (1)
ボ過給機を備えたツインターボ式内燃機関において、各
気筒群毎に高圧段排気ターボ過給機を設け、各高圧段排
気ターボ過給機と各気筒群とを繋ぐ２本の排気通路の間
に両排気通路を連通する連絡管を設け、一方の排気ター
ボ過給機にツインスクロールタービンを設け、このツイ
ンスクロールタービンに繋がる第１排気通路の前記連絡
管より下流側に第１排気通路の断面積を２分割する隔壁
を形成し、前記第１排気通路と連絡管との接続部に閉弁
時には連絡管開口を閉塞し、開弁時には連絡管を第１排
気通路の一方の分割通路に連通するように切換える第１
切換弁を設け、他方のターボ過給機に繋がる第２排気通
路と連絡管の接続部に、閉弁時には連絡管開口を閉塞し
、開弁時には第２排気通路の排気ガスの全量を連絡管へ
導くように切換える第２切換弁を設け、前記両高圧段排
気ターボ過給機の下流側にツインスクロールタービンを
有する低圧段排気ターボ過給機を１基設け、低圧段排気
ターボ過給機のツインスクロールタービンの各渦巻き室
へ前記高圧段排気ターボ過給機からの排気ガスを独立し
て導く排気接続管を設け、低圧段排気ターボ過給機から
の過給給気を両高圧段排気ターボ過給機へ導く給気接続
管を設けたことを特徴とするツインターボ式内燃機関。In a twin-turbo internal combustion engine in which multiple cylinders are divided into two groups and each cylinder group is equipped with an exhaust turbo supercharger, a high-pressure stage exhaust turbo supercharger is provided for each cylinder group, and each high-pressure stage exhaust turbo supercharger is installed in each cylinder group. A communication pipe is provided between the two exhaust passages connecting the charger and each cylinder group, and a twin scroll turbine is provided in one exhaust turbo supercharger, and a first exhaust passage is connected to the twin scroll turbine. A partition wall dividing the cross-sectional area of the first exhaust passage into two is formed on the downstream side of the communication pipe in the exhaust passage, and a partition wall is formed at the connection portion between the first exhaust passage and the communication pipe to close the communication pipe opening when the valve is closed and to open the communication pipe. At the time of valve operation, the connecting pipe is switched to communicate with one of the divided passages of the first exhaust passage.
A switching valve is provided at the connection between the second exhaust passage and the communication pipe that connects to the other turbocharger.When the valve is closed, the communication pipe opening is closed, and when the valve is opened, the entire amount of exhaust gas in the second exhaust passage is transferred to the communication pipe. A second switching valve is provided, and one low pressure stage exhaust turbo supercharger having a twin scroll turbine is provided downstream of both the high pressure stage exhaust turbo superchargers, An exhaust connection pipe is provided to independently guide the exhaust gas from the high pressure stage exhaust turbo supercharger to each spiral chamber of the twin scroll turbine, and the supercharged air from the low pressure stage exhaust turbo supercharger is connected to both high pressure stage exhaust turbo superchargers. A twin-turbo internal combustion engine characterized by a supply air connection pipe leading to a supercharger.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP63014015A JP2539655B2 (en) | 1988-01-25 | 1988-01-25 | Twin turbo type internal combustion engine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP63014015A JP2539655B2 (en) | 1988-01-25 | 1988-01-25 | Twin turbo type internal combustion engine |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH01190920A true JPH01190920A (en) | 1989-08-01 |
| JP2539655B2 JP2539655B2 (en) | 1996-10-02 |
Family
ID=11849369
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP63014015A Expired - Fee Related JP2539655B2 (en) | 1988-01-25 | 1988-01-25 | Twin turbo type internal combustion engine |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2539655B2 (en) |
Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP1221546A3 (en) * | 2001-01-05 | 2003-11-26 | Caterpillar Inc. | Two turbocharger exhaust gas re-circulation system having a first stage variable nozzle turbine |
| DE102004035323A1 (en) * | 2004-07-21 | 2006-02-16 | Bayerische Motoren Werke Ag | Sequential loader control with cylinder deactivation |
| DE102004035324A1 (en) * | 2004-07-21 | 2006-02-16 | Bayerische Motoren Werke Ag | Circuit of register charging and sequential charging |
| WO2006026742A1 (en) * | 2004-08-31 | 2006-03-09 | Government Of The United States Of America, As Represented By The Administrator Of The U.S. Environmental Protection Agency | Efficient bypass valve for multi-stage turbocharging system |
| WO2007036279A1 (en) * | 2005-09-29 | 2007-04-05 | Daimler Ag | Internal combustion engine having two exhaust gas turbochargers connected in series |
| EP1797303A2 (en) * | 2004-08-31 | 2007-06-20 | U.S. Environmental Protection Agency | Multi-stage turbocharging system with efficient bypass |
| WO2012093200A1 (en) * | 2011-01-05 | 2012-07-12 | Wärtsilä Finland Oy | A twin-turbocharger arrangement for a large internal combustion engine |
| WO2013083211A1 (en) * | 2011-12-06 | 2013-06-13 | Daimler Ag | Internal combustion engine, in particular for a motor vehicle |
| DE102005053977B4 (en) | 2005-11-11 | 2017-03-30 | Volkswagen Ag | Internal combustion engine and method for operating an internal combustion engine |
-
1988
- 1988-01-25 JP JP63014015A patent/JP2539655B2/en not_active Expired - Fee Related
Cited By (13)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP1221546A3 (en) * | 2001-01-05 | 2003-11-26 | Caterpillar Inc. | Two turbocharger exhaust gas re-circulation system having a first stage variable nozzle turbine |
| DE102004035323A1 (en) * | 2004-07-21 | 2006-02-16 | Bayerische Motoren Werke Ag | Sequential loader control with cylinder deactivation |
| DE102004035324A1 (en) * | 2004-07-21 | 2006-02-16 | Bayerische Motoren Werke Ag | Circuit of register charging and sequential charging |
| EP1797303A4 (en) * | 2004-08-31 | 2009-07-15 | Us Environmental Protection | Multi-stage turbocharging system with efficient bypass |
| EP1797303A2 (en) * | 2004-08-31 | 2007-06-20 | U.S. Environmental Protection Agency | Multi-stage turbocharging system with efficient bypass |
| WO2006026742A1 (en) * | 2004-08-31 | 2006-03-09 | Government Of The United States Of America, As Represented By The Administrator Of The U.S. Environmental Protection Agency | Efficient bypass valve for multi-stage turbocharging system |
| US7644585B2 (en) * | 2004-08-31 | 2010-01-12 | The United States Of America As Represented By The Administrator Of The U.S. Environmental Protection Agency | Multi-stage turbocharging system with efficient bypass |
| US8387385B2 (en) | 2004-08-31 | 2013-03-05 | The United States Of America, As Represented By The Administrator Of The U.S. Environmental Protection Agency | Efficient bypass valve for multi-stage turbocharging system |
| WO2007036279A1 (en) * | 2005-09-29 | 2007-04-05 | Daimler Ag | Internal combustion engine having two exhaust gas turbochargers connected in series |
| US8209982B2 (en) | 2005-09-29 | 2012-07-03 | Daimler Ag | Internal combustion engine having two exhaust gas turbochargers connected in series |
| DE102005053977B4 (en) | 2005-11-11 | 2017-03-30 | Volkswagen Ag | Internal combustion engine and method for operating an internal combustion engine |
| WO2012093200A1 (en) * | 2011-01-05 | 2012-07-12 | Wärtsilä Finland Oy | A twin-turbocharger arrangement for a large internal combustion engine |
| WO2013083211A1 (en) * | 2011-12-06 | 2013-06-13 | Daimler Ag | Internal combustion engine, in particular for a motor vehicle |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2539655B2 (en) | 1996-10-02 |
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| Date | Code | Title | Description |
|---|---|---|---|
| LAPS | Cancellation because of no payment of annual fees |