JPH0519549U - Supercharged engine - Google Patents
Supercharged engineInfo
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- JPH0519549U JPH0519549U JP7520191U JP7520191U JPH0519549U JP H0519549 U JPH0519549 U JP H0519549U JP 7520191 U JP7520191 U JP 7520191U JP 7520191 U JP7520191 U JP 7520191U JP H0519549 U JPH0519549 U JP H0519549U
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- turbine
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Abstract
(57)【要約】
【目的】 過給機付エンジンにおいて排ガス再循環（Ｅ
ＧＲ）を行いＮＯｘを低減させる。
【構成】 排気通路２から分岐し吸気通路３に接続され
る排ガス再循環路９を設け、排ガス再循環路９途中に、
エンジン本体１により駆動され排ガスの一部を吸気通路
３側へ圧送する容積型ポンプ１１を設け、吸気側と排気
側の圧力差に影響されずにＥＧＲを可能とする。
(57) [Abstract] [Purpose] Exhaust gas recirculation (E
GR) is performed to reduce NOx. [Structure] An exhaust gas recirculation passage 9 that branches from the exhaust passage 2 and is connected to the intake passage 3 is provided, and in the middle of the exhaust gas recirculation passage 9,
A positive displacement pump 11 that is driven by the engine body 1 and pumps a part of the exhaust gas to the intake passage 3 side is provided to enable EGR without being affected by the pressure difference between the intake side and the exhaust side.
Description
【０００１】[0001]
本考案は、過給機付エンジンに関するものである。 The present invention relates to a supercharged engine.
【０００２】[0002]
従来、過給機が取り付けられていない自動車のエンジンでは、エンジン本体の 排気通路から排出される排ガスの一部を、排ガス再循環路を介し排気通路と吸気 通路との間の圧力差を利用してエンジン本体の吸気通路に戻し、吸気通路に戻さ れた排ガスによりエンジン本体内での燃料の燃焼を抑制させ、燃焼温度を下げる ことによって、ＮＯｘの発生を低減するいわゆる排ガス再循環（Ｅｘｈａｕｓｔ Ｇａｓ Ｒｅｃｉｒｃｕｌａｔｉｏｎ）が行われている。 Conventionally, in an engine of an automobile without a supercharger, a part of the exhaust gas discharged from the exhaust passage of the engine body is utilized by utilizing the pressure difference between the exhaust passage and the intake passage via the exhaust gas recirculation passage. Is returned to the intake passage of the engine body, and the exhaust gas returned to the intake passage suppresses the combustion of fuel in the engine body and lowers the combustion temperature to reduce the generation of NOx, so-called exhaust gas recirculation (exhaust gas recirculation). ) Is done.
【０００３】[0003]
しかしながら、図６に示されるように、エンジン本体１から延びる排気通路２ 途中に過給機４のタービン５を設けると共にエンジン本体１への吸気通路３途中 に前記タービン５にて駆動されるコンプレッサ６を設け、前記吸気通路３におけ る前記コンプレッサ６とエンジン本体１との間にインタクーラ７を設けてなる過 給機付エンジンの場合、図７に示される如く、高負荷時には排気側よりも吸気側 の方が圧力が高くなるため、排ガス再循環を行うことができなかった。尚、図６ 中、８は過給圧が設定値を越えないよう、タービン５への流入排ガスをタービン ５の出口側にバイパスさせてタービン５の出力を制御し過給圧をコントロールす るためのウエストゲートバルブである。 However, as shown in FIG. 6, the turbine 5 of the supercharger 4 is provided in the exhaust passage 2 extending from the engine body 1, and the compressor 6 driven by the turbine 5 is provided in the intake passage 3 to the engine body 1. In the case of an engine with a supercharger in which an intercooler 7 is provided between the compressor 6 in the intake passage 3 and the engine body 1, as shown in FIG. Since the pressure was higher on the side, exhaust gas recirculation could not be performed. In FIG. 6, reference numeral 8 is for controlling the output of the turbine 5 by bypassing the exhaust gas flowing into the turbine 5 to the outlet side of the turbine 5 so that the boost pressure does not exceed the set value. It is the waste gate valve of.
【０００４】 このため、コンプレッサ６の上流側に排ガスを導くことも考えられたが、この 場合、排ガス中のカーボンによりコンプレッサ６の回転摺動部が損傷したり、イ ンタクーラ７に煤が付着して熱交換率が低下し、又、排ガスの熱によりコンプレ ッサ６の温度が上昇して該コンプレッサ６のアルミ部分のクリープ寿命が短くな る等の不具合があり、実用化は極めて困難であった。Therefore, it has been considered that the exhaust gas is guided to the upstream side of the compressor 6, but in this case, the carbon in the exhaust gas damages the rotary sliding portion of the compressor 6 or the soot adheres to the intercooler 7. The heat exchange rate is reduced, and the temperature of the compressor 6 rises due to the heat of exhaust gas, which shortens the creep life of the aluminum part of the compressor 6 and other problems. It was
【０００５】 本考案は、斯かる実情に鑑み、排ガス再循環を可能としＮＯｘ低減を図り得る 過給機付エンジンを提供しようとするものである。In view of the above situation, the present invention aims to provide an engine with a supercharger that enables exhaust gas recirculation and reduces NOx.
【０００６】[0006]
本考案は、エンジン本体よりの排気通路途中に過給機のタービンを設けると共 にエンジン本体への吸気通路途中に前記タービンにて駆動されるコンプレッサを 設け、前記コンプレッサとエンジン本体との間の吸気通路にインタクーラを設け てなる過給機付エンジンにおいて、 エンジン本体とタービンとの間の排気通路から分岐しコンプレッサとエンジン 本体との間の吸気通路に接続される排ガス再循環路途中に、排ガスの一部を吸気 通路側へ圧送する排ガス圧送ポンプを設けたことを特徴とするものである。 According to the present invention, a turbocharger turbine is provided in the exhaust passage from the engine body, and a compressor driven by the turbine is provided in the intake passage to the engine body. In an engine with a supercharger that has an intercooler in the intake passage, the exhaust gas recirculation passage that branches from the exhaust passage between the engine body and the turbine and is connected to the intake passage between the compressor and the engine body It is characterized in that an exhaust gas pressure pump for pumping a part of the gas to the intake passage side is provided.
【０００７】[0007]
従って、運転時において、排ガス圧送ポンプが駆動され、排ガスの一部が排気 通路側から吸気通路側へ圧送されるため、高負荷時に排気側よりも吸気側の圧力 が高くなっても、排ガス再循環が可能となり、ＮＯｘが低減される。 Therefore, during operation, the exhaust gas pressure pump is driven, and part of the exhaust gas is pumped from the exhaust passage side to the intake passage side.Therefore, even if the pressure on the intake side becomes higher than that on the exhaust side at high load, the exhaust gas will not be recycled. Circulation is possible and NOx is reduced.
【０００８】[0008]
以下、図面に基づいて本考案の実施例を説明する。 An embodiment of the present invention will be described below with reference to the drawings.
【０００９】 図１は本考案の第一実施例であって、図中、図６と同一の符号を付した部分は 同一物を表しており、排気通路２におけるエンジン本体１とタービン５との間か ら分岐し吸気通路３におけるコンプレッサ６とインタクーラ７との間に接続され る排ガス再循環路９を設け、該排ガス再循環路９途中に、前記エンジン本体１に よりギヤ又はベルト等の動力伝達装置１０を介して駆動され排ガスの一部を吸気 通路３側へ圧送するルーツブロワ等の容積型ポンプ１１（排ガス圧送ポンプ）を 設けると共に流量調整弁１２を設け、更に、エンジン回転数を検出する回転検出 器１３と負荷検出器１４からの検出信号１５，１６に応じて前記流量調整弁１２ に開度指令信号１７を出力する制御装置１８を設ける。FIG. 1 shows a first embodiment of the present invention. In the figure, the parts denoted by the same reference numerals as those in FIG. 6 represent the same parts, and the engine body 1 and the turbine 5 in the exhaust passage 2 are An exhaust gas recirculation path 9 that branches off from the space and is connected between the compressor 6 and the intercooler 7 in the intake path 3 is provided. A displacement type pump 11 (exhaust gas pressure pump) such as a roots blower, which is driven via the transmission device 10 and pressure-feeds a part of the exhaust gas to the intake passage 3 side, is provided with a flow rate adjusting valve 12, and the engine speed is detected. A control device 18 is provided which outputs an opening degree instruction signal 17 to the flow rate adjusting valve 12 in response to detection signals 15 and 16 from the rotation detector 13 and the load detector 14.
【００１０】 次に上記実施例の作動を説明する。Next, the operation of the above embodiment will be described.
【００１１】 運転時において、エンジン本体１により動力伝達装置１０を介して容積型ポン プ１１が駆動され、排ガスの一部が排気通路２側から吸気通路３側へ圧送される ため、図７に示されるように高負荷時に排気側よりも吸気側の圧力が高くなって も、排ガス再循環が可能となり、ＮＯｘが低減される。During operation, the displacement pump 11 is driven by the engine body 1 via the power transmission device 10, and a part of the exhaust gas is pumped from the exhaust passage 2 side to the intake passage 3 side. As shown, even when the pressure on the intake side becomes higher than that on the exhaust side at high load, exhaust gas recirculation becomes possible and NOx is reduced.
【００１２】 図２に示す如く、ＥＧＲ量を増加させるに従ってＮＯｘは低減されるが、反面 、燃費率や煙については悪化するため、本実施例においては、回転検出器１３と 負荷検出器１４により検出される検出信号１５，１６に応じて制御装置１８から 流量調整弁１２に対し開度指令信号１７が出力され、該流量調整弁１２によりＥ ＧＲ量が約２〜２０％程度の範囲内で適宜調整される。As shown in FIG. 2, NOx is reduced as the EGR amount is increased, but on the other hand, the fuel consumption rate and smoke are deteriorated. Therefore, in this embodiment, the rotation detector 13 and the load detector 14 are used. An opening command signal 17 is output from the control device 18 to the flow rate adjusting valve 12 in accordance with the detected detection signals 15 and 16, and the EGR amount is within a range of about 2 to 20% by the flow rate adjusting valve 12. It is adjusted appropriately.
【００１３】 こうして、過給機付エンジンにおいて、燃費率や煙を極端に悪化させることな く、ＮＯｘ低減を図ることが可能となる。Thus, in the engine with a supercharger, it is possible to reduce NOx without significantly deteriorating the fuel consumption rate or smoke.
【００１４】 図３は本考案の第二実施例であって、図中図１と同一の符号を付した部分は同 一のものを表わしており、エンジン本体１とタービン５との間の排気通路２から 分岐しインタークーラ７とエンジン本体１との間の吸気通路３に接続される排ガ ス再循環路９を設け、コンプレッサ６とインタクーラ７との間の吸気通路３から 分岐しタービン５より下流側の排気通路２に接続されるバイパス通路２２を設け 、該バイパス通路２２途中に小型タービン２０を設けると共に、前記排ガス再循 環路９途中に前記小型タービン２０にて駆動される小型遠心式コンプレッサ２１ （排ガス圧送ポンプ）を設けて小型ターボチャージャ１９を構成し、前記小型タ ービン２０より上流側のバイパス通路２２途中に流量調整弁２３を、小型遠心式 コンプレッサ２１より上流側の排ガス再循環路９途中に仕切弁３０を夫々設け、 更に、エンジン回転数を検出する回転検出器１３と負荷検出器１４からの検出信 号１５，１６に応じて、前記仕切弁３０に開閉指令信号３１を、前記流量調整弁 ２３に開度指令信号２４を夫々出力する制御装置１８を設ける。FIG. 3 shows a second embodiment of the present invention, in which the same reference numerals as in FIG. 1 denote the same parts, and the exhaust gas between the engine body 1 and the turbine 5 is shown. An exhaust gas recirculation path 9 that branches from the passage 2 and is connected to the intake passage 3 between the intercooler 7 and the engine body 1 is provided, and branches from the intake passage 3 between the compressor 6 and the intercooler 7 that branches from the turbine 5 A bypass passage 22 connected to the exhaust passage 2 on the more downstream side is provided, a small turbine 20 is provided in the middle of the bypass passage 22, and a small centrifugal driven by the small turbine 20 is provided in the exhaust gas recirculation passage 9. A compact compressor 21 (exhaust gas pressure pump) is provided to form a small turbocharger 19, and a flow control valve 23 is provided in the middle of a bypass passage 22 upstream of the small turbine 20. A sluice valve 30 is provided in the middle of the exhaust gas recirculation path 9 upstream of the compressor 21, and further, according to the detection signals 15 and 16 from the rotation detector 13 and the load detector 14 for detecting the engine speed, A control device 18 for outputting an opening / closing command signal 31 to the sluice valve 30 and an opening command signal 24 to the flow rate adjusting valve 23 is provided.
【００１５】 図３に示す実施例の場合、運転時において、回転検出器１３と負荷検出器１４ により検出される検出信号１５，１６に応じて制御装置１８から仕切弁３０に対 し開閉指令信号３１が、流量調整弁２３に対し開度指令信号２４が夫々出力され 、仕切弁３０が開き、流量調整弁２３が開くと、吸気通路３から吸気の一部がバ イパス通路２２へ分岐し、小型タービン２０が駆動され、該小型タービン２０に より小型遠心式コンプレッサ２１が駆動され、排ガスの一部が排気通路２側から 吸気通路３側へ圧送されるため、図７に示されるように高負荷時に排気側よりも 吸気側の圧力が高くなっても、排ガス再循環が可能となり、ＮＯｘが低減される 。In the case of the embodiment shown in FIG. 3, during operation, the control device 18 sends an opening / closing command signal to the sluice valve 30 in response to the detection signals 15 and 16 detected by the rotation detector 13 and the load detector 14. When the opening degree command signal 24 is output to the flow rate adjusting valve 23, the sluice valve 30 is opened, and the flow rate adjusting valve 23 is opened, a part of the intake air is branched from the intake passage 3 to the bypass passage 22. The small turbine 20 is driven, the small centrifugal compressor 21 is driven by the small turbine 20, and a part of the exhaust gas is pumped from the exhaust passage 2 side to the intake passage 3 side. Therefore, as shown in FIG. Even when the pressure on the intake side becomes higher than that on the exhaust side during load, exhaust gas recirculation becomes possible and NOx is reduced.
【００１６】 又、ＥＧＲ量については、燃費率や煙を極端に悪化させることのないよう、流 量調整弁２３の開度調整による小型タービン２０の回転制御により、約２〜２０ ％程度の範囲内で適宜調整される。Further, the EGR amount is in the range of about 2 to 20% by controlling the rotation of the small turbine 20 by adjusting the opening degree of the flow rate adjusting valve 23 so as not to significantly deteriorate the fuel consumption rate and smoke. It is adjusted appropriately within.
【００１７】 尚、図３中に示す実施例において、バイパス通路２２を、タービン５より下流 側の排気通路２に接続する代わりに、図３中仮想線で示す如くコンプレッサ６よ り上流側の吸気通路３に接続することも可能である。In the embodiment shown in FIG. 3, instead of connecting the bypass passage 22 to the exhaust passage 2 on the downstream side of the turbine 5, the intake air on the upstream side of the compressor 6 is indicated by a phantom line in FIG. It is also possible to connect to the passage 3.
【００１８】 図４は本考案の第三実施例であって、図中図３と同一の符号を付した部分は同 一のものを表わしており、バイパス通路２２を吸気通路３から分岐させる代りに 、エンジン本体１とタービン５との間の排気通路２から分岐させたものである。FIG. 4 shows a third embodiment of the present invention, in which the parts designated by the same reference numerals as those in FIG. 3 represent the same parts, and instead of branching the bypass passage 22 from the intake passage 3, First, the exhaust passage 2 between the engine body 1 and the turbine 5 is branched.
【００１９】 図４に示す実施例の場合、運転時において、回転検出器１３と負荷検出器１４ により検出される検出信号１５，１６に応じて制御装置１８から仕切弁３０に対 し開閉指令信号３１が、流量調整弁２３に対し開度指令信号２４が夫々出力され 、仕切弁３０が開き、流量調整弁２３が開くと、排気通路２から排気の一部がバ イパス通路２２へ分岐し、小型タービン２０が駆動され、該小型タービン２０に より小型遠心式コンプレッサ２１が駆動され、排ガスの一部が排気通路２側から 吸気通路３側へ圧送されるため、図７に示されるように高負荷時に排気側よりも 吸気側の圧力が高くなっても、排ガス再循環が可能となり、ＮＯｘが低減される 。In the case of the embodiment shown in FIG. 4, during operation, the controller 18 sends an opening / closing command signal to the sluice valve 30 in response to the detection signals 15 and 16 detected by the rotation detector 13 and the load detector 14. When the opening degree command signal 24 is output to the flow rate adjusting valve 23, the sluice valve 30 opens, and the flow rate adjusting valve 23 opens, a part of the exhaust gas branches from the exhaust passage 2 to the bypass passage 22. The small turbine 20 is driven, the small centrifugal compressor 21 is driven by the small turbine 20, and a part of the exhaust gas is pumped from the exhaust passage 2 side to the intake passage 3 side. Therefore, as shown in FIG. Even when the pressure on the intake side becomes higher than that on the exhaust side during load, exhaust gas recirculation becomes possible and NOx is reduced.
【００２０】 又、ＥＧＲ量については、図３に示す実施例の場合と同様に、燃費率や煙を極 端に悪化させることのないよう、流量調整弁２３の開度調整による小型タービン ２０の回転制御により、約２〜２０％程度の範囲内で適宜調整される。Regarding the EGR amount, as in the case of the embodiment shown in FIG. 3, the small turbine 20 is adjusted by adjusting the opening degree of the flow rate adjusting valve 23 so as to prevent the fuel efficiency and smoke from being extremely deteriorated. By rotation control, it is appropriately adjusted within a range of about 2 to 20%.
【００２１】 図５は本考案の第四実施例であって、図中図１と同一の符号を付した部分は同 一のものを表わしており、エンジン本体１とタービン５との間の排気通路２から 分岐しインタクーラ７とエンジン本体１との間の吸気通路３に接続される排ガス 再循環路９を設け、エンジン本体１から逆止弁３５を介して供給される圧油の循 環通路２５途中に、エンジン本体１によりクラッチ２７を介して駆動される油圧 ポンプ２６と、油圧タービン２８とを設け、前記排ガス再循環路９途中に、油圧 タービン２８にて駆動される遠心式コンプレッサ２９（排ガス圧送ポンプ）を設 け、該遠心式コンプレッサ２９より上流側の排ガス再循環路９途中に仕切弁３０ を設け、前記油圧タービンの上下流側の循環通路を、途中に流量調整弁３３が設 けられたバイパス通路３２にて短絡せしめ、エンジン回転数を検出する回転検出 器１３と負荷検出器１４からの検出信号１５，１６に応じて、前記クラッチ２７ にオンオフ指令信号３６を、前記仕切弁３０に開閉指令信号３１を、前記流量調 整弁３３に開度指令信号３４を夫々出力する制御装置１８を設ける。FIG. 5 shows a fourth embodiment of the present invention, in which the same reference numerals as in FIG. 1 denote the same parts, and the exhaust gas between the engine body 1 and the turbine 5 is shown. An exhaust gas recirculation passage 9 that branches from the passage 2 and is connected to the intake passage 3 between the intercooler 7 and the engine body 1 is provided, and a circulation passage for pressure oil supplied from the engine body 1 through the check valve 35. A hydraulic pump 26 driven by the engine body 1 via the clutch 27 and a hydraulic turbine 28 are provided in the middle of 25, and a centrifugal compressor 29 (driven by the hydraulic turbine 28 in the middle of the exhaust gas recirculation path 9 ( Exhaust gas pressure pump), a sluice valve 30 in the exhaust gas recirculation path 9 upstream of the centrifugal compressor 29, a circulation passage in the upstream and downstream of the hydraulic turbine, and a flow rate adjustment valve 33 in the middle. Ke The bypass passage 32 is short-circuited, and the ON / OFF command signal 36 is sent to the clutch 27 according to the detection signals 15 and 16 from the rotation detector 13 and the load detector 14 for detecting the engine speed. A control device 18 for outputting an opening / closing command signal 31 and an opening command signal 34 to the flow rate adjusting valve 33 is provided.
【００２２】 図５に示す実施例の場合、運転時において、回転検出器１３と負荷検出器１４ により検出される検出信号１５，１６に応じて制御装置１８からクラッチ２７に オンオフ指令信号３６が、仕切弁３０に開閉指令信号３１が、流量調整弁３３に 開度指令信号３４が夫々出力され、クラッチ２７がオンとなり、仕切弁３０が開 き、流量調整弁２３が所要の開度で開くと、クラッチ２７を介して駆動される油 圧ポンプ２６により圧油が循環通路２５を流れると共に流量調整弁３３の開度に 応じて油圧タービン２８に供給される圧油の量が調整され、油圧タービン２８が 駆動され、該油圧タービン２８により遠心式コンプレッサ２９が駆動され、燃費 率や煙を極端に悪化させない程度の量の排ガスが排気通路２側から吸気通路３側 へ圧送され、図７に示されるように高負荷時に排気側よりも吸気側の圧力が高く なっても、排ガス再循環が可能となり、ＮＯｘが低減される。In the case of the embodiment shown in FIG. 5, during operation, an on / off command signal 36 from the control device 18 to the clutch 27 according to the detection signals 15 and 16 detected by the rotation detector 13 and the load detector 14, When the opening / closing command signal 31 is output to the gate valve 30 and the opening command signal 34 is output to the flow rate adjusting valve 33, the clutch 27 is turned on, the gate valve 30 is opened, and the flow rate adjusting valve 23 is opened at a required opening degree. , The hydraulic pump 26 driven via the clutch 27 causes the hydraulic oil to flow through the circulation passage 25, and the amount of the hydraulic oil supplied to the hydraulic turbine 28 is adjusted according to the opening degree of the flow rate adjusting valve 33. 28 is driven, and the centrifugal compressor 29 is driven by the hydraulic turbine 28, so that an amount of exhaust gas from the exhaust passage 2 side to the intake passage 3 side is large enough not to significantly deteriorate the fuel efficiency and smoke. Even if the pressure is fed and the pressure on the intake side becomes higher than that on the exhaust side at the time of high load as shown in FIG. 7, exhaust gas recirculation becomes possible and NOx is reduced.
【００２３】 尚、本考案の過給機付エンジンは、上述の実施例にのみ限定されるものではな く、第一実施例における排ガス圧送ポンプとしての容積型ポンプをエンジン本体 によりギヤ又はベルト等の動力伝達装置を介して駆動する代わりに、第二、第三 実施例の如く吸気又は排気利用のタービンによって駆動したり、或いは第四実施 例の如く油圧タービンによって駆動するようにしてもよいこと、第二、第三、第 四実施例における排ガス圧送ポンプとしての遠心式コンプレッサを第一実施例の 如くエンジン本体によりギヤ又はベルト等の動力伝達装置を介して駆動するよう にしてもよいこと、その他、本考案の要旨を逸脱しない範囲内において種々変更 を加え得ることは勿論である。The engine with a supercharger of the present invention is not limited to the above-mentioned embodiment, but the displacement type pump as the exhaust gas pressure pump in the first embodiment is provided with a gear or a belt by the engine body. Instead of being driven via the power transmission device of the second embodiment, it may be driven by a turbine utilizing intake air or exhaust gas as in the second and third embodiments, or may be driven by a hydraulic turbine as in the fourth embodiment. The centrifugal compressor as the exhaust gas pressure pump in the second, third, and fourth embodiments may be driven by the engine body via a power transmission device such as a gear or a belt as in the first embodiment. Of course, various changes can be made without departing from the scope of the present invention.
【００２４】[0024]
以上説明したように本考案の過給機付エンジンによれば、従来不可能であった 排ガス再循環が可能となり、燃費率や煙の悪化を抑えつつＮＯｘ低減を図れると いう優れた効果を奏し得る。 As described above, the engine with a supercharger of the present invention enables exhaust gas recirculation, which has been impossible in the past, and has an excellent effect that NOx can be reduced while suppressing deterioration of fuel efficiency and smoke. obtain.
【図１】本考案の第一実施例の系統図である。FIG. 1 is a system diagram of a first embodiment of the present invention.
【図２】ＥＧＲ量と、ＮＯｘ、燃費率、煙との関係を示
す線図である。FIG. 2 is a diagram showing a relationship among an EGR amount, NOx, a fuel consumption rate, and smoke.
【図３】本考案の第二実施例の系統図である。FIG. 3 is a system diagram of a second embodiment of the present invention.
【図４】本考案の第三実施例の系統図である。FIG. 4 is a system diagram of a third embodiment of the present invention.
【図５】本考案の第四実施例の系統図である。FIG. 5 is a system diagram of a fourth embodiment of the present invention.
【図６】一般的な過給機付エンジンの系統図である。FIG. 6 is a system diagram of a general engine with a supercharger.
【図７】過給機付エンジンにおける負荷と圧力との関係
を示す線図である。FIG. 7 is a diagram showing a relationship between load and pressure in a supercharged engine.
１ エンジン本体 ２ 排気通路 ３ 吸気通路 ４ 過給機 ５ タービン ６ コンプレッサ ７ インタクーラ ９ 排ガス再循環路 １１ 容積型ポンプ（排ガス圧送ポンプ） １２ 流量調整弁 １３ 回転検出器 １４ 負荷検出器 １７ 開度指令信号 １８ 制御装置 １９ 小型ターボチャージャ ２０ 小型タービン ２１ 小型遠心式コンプレッサ（排ガス圧送ポンプ） ２２ バイパス通路 ２３ 流量調整弁 ２４ 開度指令信号 ２５ 循環通路 ２６ 油圧ポンプ ２７ クラッチ ２８ 油圧タービン ２９ 遠心式コンプレッサ（排ガス圧送ポンプ） ３０ 仕切弁 ３１ 開閉指令信号 ３２ バイパス通路 ３３ 流量調整弁 ３４ 開度指令信号 ３６ オンオフ指令信号 1 Engine Main Body 2 Exhaust Passage 3 Intake Passage 4 Supercharger 5 Turbine 6 Compressor 7 Intercooler 9 Exhaust Gas Recirculation Route 11 Positive Displacement Pump (Exhaust Gas Pressure Pump) 12 Flow Control Valve 13 Rotation Detector 14 Load Detector 17 Opening Command Signal 18 Control Device 19 Small Turbocharger 20 Small Turbine 21 Small Centrifugal Compressor (Exhaust Gas Pump) 22 Bypass Passage 23 Flow Control Valve 24 Opening Command Signal 25 Circulation Passage 26 Hydraulic Pump 27 Clutch 28 Hydraulic Turbine 29 Centrifugal Compressor (Exhaust Gas Pressure Feed) Pump) 30 Gate valve 31 Opening / closing command signal 32 Bypass passage 33 Flow rate adjusting valve 34 Opening command signal 36 On / off command signal
Claims (1)
機のタービンを設けると共にエンジン本体への吸気通路
途中に前記タービンにて駆動されるコンプレッサを設
け、前記コンプレッサとエンジン本体との間の吸気通路
にインタクーラを設けてなる過給機付エンジンにおい
て、 エンジン本体とタービンとの間の排気通路から分岐しコ
ンプレッサとエンジン本体との間の吸気通路に接続され
る排ガス再循環路途中に、排ガスの一部を吸気通路側へ
圧送する排ガス圧送ポンプを設けたことを特徴とする過
給機付エンジン。1. A turbocharger turbine is provided in the exhaust passage from the engine body, and a compressor driven by the turbine is provided in the intake passage to the engine body, and intake air between the compressor and the engine body is provided. In an engine with a supercharger that has an intercooler in the passage, in the middle of the exhaust gas recirculation passage that branches from the exhaust passage between the engine body and the turbine and is connected to the intake passage between the compressor and the engine body, An engine with a supercharger, which is equipped with an exhaust gas pressure pump that pumps a portion of it to the intake passage side.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP7520191U JPH0519549U (en) | 1991-08-26 | 1991-08-26 | Supercharged engine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP7520191U JPH0519549U (en) | 1991-08-26 | 1991-08-26 | Supercharged engine |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH0519549U true JPH0519549U (en) | 1993-03-12 |
Family
ID=13569347
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP7520191U Pending JPH0519549U (en) | 1991-08-26 | 1991-08-26 | Supercharged engine |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH0519549U (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH06137220A (en) * | 1992-10-28 | 1994-05-17 | Unisia Jecs Corp | Exhaust gas recirculation control device for internal combustion engine |
Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5741456A (en) * | 1980-08-21 | 1982-03-08 | Kee Aya Kajimu | Turbocharge engine with recirculation of compressed gas |
| JPS6189968A (en) * | 1984-10-09 | 1986-05-08 | Isuzu Motors Ltd | Suction heater for internal-combustion engine |
| JPH03117665A (en) * | 1989-09-29 | 1991-05-20 | Hino Motors Ltd | Egr device of turbosupercharge engine |
-
1991
- 1991-08-26 JP JP7520191U patent/JPH0519549U/en active Pending
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5741456A (en) * | 1980-08-21 | 1982-03-08 | Kee Aya Kajimu | Turbocharge engine with recirculation of compressed gas |
| JPS6189968A (en) * | 1984-10-09 | 1986-05-08 | Isuzu Motors Ltd | Suction heater for internal-combustion engine |
| JPH03117665A (en) * | 1989-09-29 | 1991-05-20 | Hino Motors Ltd | Egr device of turbosupercharge engine |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH06137220A (en) * | 1992-10-28 | 1994-05-17 | Unisia Jecs Corp | Exhaust gas recirculation control device for internal combustion engine |
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