WO2012101737A1 - 過給機付き内燃機関の制御装置 - Google Patents
過給機付き内燃機関の制御装置 Download PDFInfo
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- WO2012101737A1 WO2012101737A1 PCT/JP2011/051212 JP2011051212W WO2012101737A1 WO 2012101737 A1 WO2012101737 A1 WO 2012101737A1 JP 2011051212 W JP2011051212 W JP 2011051212W WO 2012101737 A1 WO2012101737 A1 WO 2012101737A1
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- blow
- amount
- exhaust
- valve
- overlap period
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
- F02B37/12—Control of the pumps
- F02B37/18—Control of the pumps by bypassing exhaust from the inlet to the outlet of turbine or to the atmosphere
- F02B37/183—Arrangements of bypass valves or actuators therefor
-
- 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
- F02B25/00—Engines characterised by using fresh charge for scavenging cylinders
- F02B25/14—Engines characterised by using fresh charge for scavenging cylinders using reverse-flow scavenging, e.g. with both outlet and inlet ports arranged near bottom of piston stroke
- F02B25/145—Engines characterised by using fresh charge for scavenging cylinders using reverse-flow scavenging, e.g. with both outlet and inlet ports arranged near bottom of piston stroke with intake and exhaust valves exclusively in the cylinder head
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
- F02B37/12—Control of the pumps
- F02B37/18—Control of the pumps by bypassing exhaust from the inlet to the outlet of turbine or to the atmosphere
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D13/00—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing
- F02D13/02—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing during engine operation
- F02D13/0203—Variable control of intake and exhaust valves
- F02D13/0215—Variable control of intake and exhaust valves changing the valve timing only
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D13/00—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing
- F02D13/02—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing during engine operation
- F02D13/0261—Controlling the valve overlap
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D23/00—Controlling engines characterised by their being supercharged
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D41/00—Electrical control of supply of combustible mixture or its constituents
- F02D41/0002—Controlling intake air
- F02D41/0007—Controlling intake air for control of turbo-charged or super-charged engines
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D41/00—Electrical control of supply of combustible mixture or its constituents
- F02D41/0025—Controlling engines characterised by use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures
- F02D41/0047—Controlling exhaust gas recirculation [EGR]
- F02D41/0065—Specific aspects of external EGR control
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D41/00—Electrical control of supply of combustible mixture or its constituents
- F02D41/0002—Controlling intake air
- F02D2041/001—Controlling intake air for engines with variable valve actuation
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D41/00—Electrical control of supply of combustible mixture or its constituents
- F02D41/02—Circuit arrangements for generating control signals
- F02D41/021—Introducing corrections for particular conditions exterior to the engine
- F02D41/0235—Introducing corrections for particular conditions exterior to the engine in relation with the state of the exhaust gas treating apparatus
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D41/00—Electrical control of supply of combustible mixture or its constituents
- F02D41/02—Circuit arrangements for generating control signals
- F02D41/18—Circuit arrangements for generating control signals by measuring intake air flow
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- 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
Definitions
- the present invention relates to a control device for an internal combustion engine with a supercharger, and in particular, a supercharger suitable for controlling an internal combustion engine having a variable valve mechanism and a wastegate valve that can change a valve overlap period.
- the present invention relates to an internal combustion engine control apparatus.
- Patent Document 1 discloses a control device for an internal combustion engine.
- the amount of fresh air blown from the intake passage through the combustion chamber to the exhaust passage is estimated based on the oxygen concentration in the exhaust passage detected by the air-fuel ratio sensor.
- the valve overlap period is controlled in accordance with the amount of fresh air blown through.
- Japanese Unexamined Patent Publication No. 2007-263083 Japanese Unexamined Patent Publication No. 2008-175201 Japanese Unexamined Patent Publication No. 2010-163915 Japanese Unexamined Patent Publication No. 2008-297930
- the blow-through amount can be reduced by reducing the valve overlap period when the blow-through amount of fresh air is large.
- operation regions in which it is difficult to reduce the blow-through amount to a desired amount only by adjusting the valve overlap period. In such an operation region, it is not possible to satisfactorily reduce the blow-through amount only by reducing the valve overlap period, and as a result, the catalyst may be overheated.
- the present invention has been made to solve the above-described problems, and overheating of a catalyst disposed in an exhaust passage is caused when blow-through of fresh air from the intake passage to the exhaust passage through the combustion chamber occurs. It is an object of the present invention to provide a control device for an internal combustion engine with a supercharger capable of suitably achieving both prevention and suppression of turbo lag.
- 1st invention is a control apparatus of the internal combustion engine with a supercharger, A turbocharger having a turbine operating by exhaust energy in the exhaust passage; An exhaust bypass passage that branches off from the exhaust passage at a portion upstream of the turbine and merges with the exhaust passage at a portion downstream of the turbine; A waste gate valve capable of switching opening and closing of the exhaust bypass passage; A variable valve mechanism capable of changing a valve overlap period in which an exhaust valve opening period and an intake valve opening period overlap; Blow-through amount acquisition means for acquiring a blow-through amount of fresh air from the intake passage through the combustion chamber to the exhaust passage; An overlap period reducing means for reducing the valve overlap period so that the blow-through amount is equal to or less than the blow-through determination value when the blow-through amount is larger than a predetermined blow-through determination value; Blow-through amount determination means for determining whether or not the blow-through amount is still larger than the blow-through determination value after the valve overlap period is reduced by the overlap period reduction means; WGV control means for opening the waste gate valve when the
- the second invention is the first invention, wherein An air-fuel ratio sensor disposed in the exhaust passage and detecting an air-fuel ratio of the exhaust gas;
- the blow-by amount acquisition means is means for acquiring the blow-through amount based on an output value of the air-fuel ratio sensor.
- the blow-off amount is reduced below the blow-through determination value while suppressing the opening control amount of the waste gate valve to the necessary minimum. be able to. Therefore, according to the present invention, when the blow-through amount is larger than the blow-through determination value, it is possible to suitably achieve both the prevention of catalyst overheating by the suppression of the blow-through amount and the suppression of the turbo lag.
- the catalyst when the blow-through amount is larger than the blow-through determination value, the catalyst is prevented from being overheated by suppressing the blow-through amount using the configuration for acquiring the blow-through amount based on the output value of the air-fuel ratio sensor.
- the turbo lag it is possible to achieve both suppression of the turbo lag suitably.
- Embodiment 1 of this invention It is a schematic diagram for demonstrating the system configuration
- FIG. 1 is a schematic diagram for explaining a system configuration of an internal combustion engine 10 according to a first embodiment of the present invention.
- the system of the present embodiment includes a spark ignition type internal combustion engine (gasoline engine) 10 as an example.
- a combustion chamber 12 is formed in the cylinder of the internal combustion engine 10.
- An intake passage 14 and an exhaust passage 16 communicate with the combustion chamber 12.
- An air cleaner 18 is attached in the vicinity of the inlet of the intake passage 14.
- An air flow meter 20 that outputs a signal corresponding to the flow rate of air sucked into the intake passage 14 is provided in the vicinity of the downstream side of the air cleaner 18.
- a compressor 22 a of the turbocharger 22 is installed downstream of the air flow meter 20.
- the compressor 22a is integrally connected via a turbine 22b and a turbine shaft 22c disposed in the exhaust passage 16.
- An intercooler 24 for cooling the compressed air is provided downstream of the compressor 22a.
- An electronically controlled throttle valve 26 is provided downstream of the intercooler 24.
- An intake pressure sensor 28 for detecting the intake pressure P1 is disposed downstream of the throttle valve 26 (intake manifold portion).
- Each cylinder of the internal combustion engine 10 is provided with a fuel injection valve 30 for injecting fuel into the intake port and an ignition plug 32 for igniting the air-fuel mixture.
- an air-fuel ratio sensor 34 for detecting the air-fuel ratio (oxygen concentration) of the exhaust gas is disposed upstream of the turbine 22b in the exhaust passage 16.
- an exhaust bypass passage 36 is connected to the exhaust passage 16 so as to branch from the exhaust passage 16 at a portion upstream of the turbine 22b and to merge with the exhaust passage 16 at a portion downstream of the turbine 22b.
- a waste gate valve (WGV) 38 that opens and closes the exhaust bypass passage 36 is provided in the middle of the exhaust bypass passage 36.
- WGV 38 is configured to be adjustable to an arbitrary opening degree by a pressure-regulating or electric actuator (not shown).
- a catalyst 40 for purifying exhaust gas is disposed in the exhaust passage 16 further downstream than the connection portion with the exhaust bypass passage 36 downstream of the turbine 22b.
- the intake port and the exhaust port are respectively provided with an intake valve 42 and an exhaust valve 44 for bringing the combustion chamber 12 and the intake passage 14 or the combustion chamber 12 and the exhaust passage 16 into a conductive state or a cut-off state.
- the intake valve 42 and the exhaust valve 44 are driven by an intake variable valve mechanism 46 and an exhaust variable valve mechanism 48, respectively.
- the variable intake valve mechanism 46 is a variable valve timing (VVT) mechanism that continuously varies the opening / closing timing of the intake valve 42 by changing the rotation phase of the intake camshaft relative to the rotation phase of the crankshaft.
- VVT variable valve timing
- the exhaust variable valve mechanism 48 has a similar configuration.
- an intake cam angle sensor 50 and an exhaust cam angle sensor 52 for detecting the rotation angles of the respective cam shafts, that is, the intake cam angle and the exhaust cam angle are arranged in the vicinity of the intake cam shaft and the exhaust cam shaft, respectively. Has been.
- the system shown in FIG. 1 includes an ECU (Electronic Control Unit) 54.
- ECU Electronic Control Unit
- an input portion of the ECU 54 is used for detecting the operating state of the internal combustion engine 10 such as a crank angle sensor 56 for detecting the engine speed.
- Various sensors are connected.
- Various actuators for controlling the operating state of the internal combustion engine 10 such as the throttle valve 26, the fuel injection valve 30, the spark plug 32, the WGV 38, and the variable valve mechanisms 46 and 48 are connected to the output portion of the ECU 54.
- the ECU 54 controls the operating state of the internal combustion engine 10 by operating various actuators according to a predetermined program based on the outputs of the various sensors described above.
- FIG. 2 is a view for explaining blow-through of fresh air from the intake passage 14 to the exhaust passage 16 through the combustion chamber 12.
- the intake variable valve mechanism 46 and the exhaust variable valve mechanism 48 described above by adjusting at least one of the advance amount of the open / close timing of the intake valve 42 and the retard amount of the open / close timing of the exhaust valve 44.
- the length of the valve overlap period (hereinafter simply referred to as “valve overlap period”) in which the valve opening period of the exhaust valve 44 and the valve opening period of the intake valve 42 overlap can be changed.
- the output value of the air-fuel ratio sensor 34 is used to calculate the fresh air blow-through amount Gsca, and the calculated blow-through amount Gsca is a predetermined blow-through determination value.
- the valve overlap period is shortened so that the blow-through amount Gsca becomes equal to or smaller than the blow-through determination value Gjudge.
- the WGV 38 is opened when the blow-through amount Gsca is still not equal to or less than the blow-through determination value Gjudge.
- FIG. 3 is a flowchart showing a control routine executed by the ECU 54 in order to realize the control in the first embodiment of the present invention.
- the routine shown in FIG. 3 first, it is determined whether or not a fresh air blow-out occurrence condition is satisfied (step 100).
- the ECU 54 has a blow-through occurrence condition in which a fresh air blow-out occurs during the setting of the valve overlap period in relation to the operation region of the internal combustion engine 10 (region based on the load factor and the engine speed).
- region which is formed is memorize
- this step 100 it is determined with reference to such a map whether or not the current operation region is an operation region in which the blow-out occurrence condition is satisfied.
- the determination of whether or not the blow-through occurrence condition is satisfied is not limited to the above method. For example, if the exhaust pressure sensor that detects the exhaust pressure P2 is provided together with the intake pressure sensor 28 that detects the intake pressure P1, You may perform by comparing those sensor values.
- the fresh air blow-off amount Gsca is calculated based on the output value of the air-fuel ratio sensor 34 (step 102).
- the blow-through amount Gsca is calculated according to the following equation.
- Gsca Sabyf / Iabif ⁇ Ga
- Sabyf the air-fuel ratio of the exhaust gas acquired using the air-fuel ratio sensor 34
- Ibyf the target air-fuel ratio calculated based on the intake air amount and the fuel injection amount.
- Ga is the amount of intake air acquired using the air flow meter 20.
- step 104 it is determined whether or not the valve overlap period is being reduced. Specifically, in this step 104, it is determined whether or not the valve overlap period is reduced to a predetermined value or less by the process of step 108 described later while the above-described blow-through occurrence condition is established. .
- step 106 If it is determined in step 104 that the valve overlap period is not being reduced, it is determined whether or not the fresh air blowing amount Gsca is greater than a predetermined determination value Gjudge (step 106).
- the determination value Gjudge in this step 106 is a value set in advance as a threshold value for determining whether or not the current blow-through amount Gsca is an amount that causes the catalyst 40 to overheat.
- step 106 If it is determined in step 106 that the current blow-through amount Gsca is larger than the determination value Gjudge, the variable valve mechanisms 46 and 48 are reduced so that the valve overlap period becomes a predetermined value or less. (Step 108).
- step 110 determines whether or not the current blow-through amount Gsca is greater than the determination value Gjudge is determined by the same processing as in step 106.
- a determination is made (step 110). As a result, if it is determined in step 110 that the current blow-through amount Gsca is larger than the determination value Gjudge, that is, the blow-off amount Gsca is still less than or equal to the blow-out determination value Gjudge even though the valve overlap period is reduced. If it can be determined that it is not, the WGV 38 is opened to an opening for lowering the supercharging pressure below a predetermined pressure (step 112). The process of this step 112 can be performed as follows as an example.
- the WGV is opened so that the blow-through amount Gsca becomes a supercharging pressure value (obtained from a map or the like) that is necessary to make the blow-through amount determination value Gjudge or less.
- Feedback control based on the intake pressure P1 detected by the intake pressure sensor 28, the WGV is opened so that the blow-through amount Gsca becomes a supercharging pressure value (obtained from a map or the like) that is necessary to make the blow-through amount determination value Gjudge or less.
- the WGV 38 is opened to lower the supercharging pressure when the blow-through amount Gsca is not yet equal to or smaller than the blow-through determination value Gjudge after the valve overlap period is reduced. That is, according to the above routine, under the situation where the blow-through amount Gsca is larger than the blow-through determination value Gjudge, control for reducing the blow-through amount Gsca is performed in the order of reducing the valve overlap period and then adjusting the WGV 38. Is done.
- the opening degree control amount of the WGV 38 necessary to make the blow-through amount Gsca become equal to or smaller than the blow-through determination value Gjudge. growing. As a result, the turbo lag becomes large due to a decrease in the flow rate of the exhaust gas passing through the turbine 22b.
- the opening degree control amount of the WGV 38 can be suppressed to a necessary minimum.
- the blow-through amount Gsca when the blow-through amount Gsca is larger than the blow-through determination value Gjudge, the scavenging action can be obtained, and the overheating of the catalyst 40 can be prevented by suppressing the blow-through amount Gsca. It is possible to achieve both suppression and compatibility.
- the amount of fresh air blown is calculated using the output value of the air-fuel ratio sensor 34.
- the blow-by amount acquisition means in the present invention is not limited to the one using the above method.
- the intake variable valve mechanism 46 that can change the opening / closing timing of the intake valve 42 and the exhaust variable valve mechanism 48 that can change the opening / closing timing of the exhaust valve 44 are used.
- the valve overlap period is changed.
- the variable valve mechanism in the present invention is not limited to the above-described configuration. That is, the valve overlap period may be adjusted by adjusting at least one of the closing timing of the exhaust valve and the opening timing of the intake valve.
- the “blow-through amount acquisition means” in the first aspect of the present invention determines that the determination of step 106 is true.
- the “overlap period reduction means” in the first invention executes the process in the step 110 when the determination in the step 104 is satisfied.
- the “WGV control means” according to the first aspect of the present invention is realized by executing the processing of step 112 when the determination of step 110 is established.
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Abstract
Description
尚、出願人は、本発明に関連するものとして、上記の文献を含めて、以下に記載する文献を認識している。
排気エネルギーにより作動するタービンを排気通路に備えるターボ過給機と、
前記タービンよりも上流側の部位において前記排気通路から分岐し、前記タービンよりも下流側の部位において前記排気通路と合流する排気バイパス通路と、
前記排気バイパス通路の開閉を切り替え可能なウェイストゲートバルブと、
排気弁の開弁期間と吸気弁の開弁期間とが重なるバルブオーバーラップ期間を変更可能とする可変動弁機構と、
燃焼室を介した吸気通路から前記排気通路への新気の吹き抜け量を取得する吹き抜け量取得手段と、
前記吹き抜け量が所定の吹き抜け判定値よりも多い場合に、当該吹き抜け量が前記吹き抜け判定値以下となるように前記バルブオーバーラップ期間を縮小させるオーバーラップ期間縮小手段と、
前記オーバーラップ期間縮小手段により前記バルブオーバーラップ期間が縮小された後に前記吹き抜け量が未だ前記吹き抜け判定値よりも多いか否かを判定する吹き抜け量判定手段と、
前記吹き抜け量判定手段により前記吹き抜け量が未だ前記吹き抜け判定値よりも多いと判定された場合に、前記ウェイストゲートバルブを開くWGV制御手段と、
を備えることを特徴とする。
前記排気通路に配置され、排気ガスの空燃比を検出する空燃比センサを更に備え、
前記吹き抜け量取得手段は、前記空燃比センサの出力値に基づいて前記吹き抜け量を取得する手段であることを特徴とする。
[システム構成の説明]
図1は、本発明の実施の形態1の内燃機関10のシステム構成を説明するための模式図である。本実施形態のシステムは、一例として火花点火式の内燃機関(ガソリンエンジン)10を備えている。内燃機関10の筒内には、燃焼室12が形成されている。燃焼室12には、吸気通路14および排気通路16が連通している。
図2は、燃焼室12を介した吸気通路14から排気通路16への新気の吹き抜けを説明するための図である。
上述した吸気可変動弁機構46および排気可変動弁機構48によれば、吸気弁42の開閉時期の進角量と排気弁44の開閉時期の遅角量のうちの少なくとも一方を調整することにより、排気弁44の開弁期間と吸気弁42の開弁期間とが重なるバルブオーバーラップ期間(以下、単に「バルブオーバーラップ期間」という)の長さを変化させることができる。
図3に示すルーチンでは、先ず、新気の吹き抜け発生条件であるか否かが判定される(ステップ100)。具体的には、ECU54は、内燃機関10の運転領域(負荷率とエンジン回転数とに基づく領域)との関係で、バルブオーバーラップ期間の設定中に新気の吹き抜けが発生する吹き抜け発生条件が成立する運転領域を規定したマップ(図示省略)を記憶している。本ステップ100では、そのようなマップを参照して、現在の運転領域が、吹き抜け発生条件が成立する運転領域であるか否かが判定される。尚、吹き抜け発生条件の成立の有無の判定は、上記手法に限らず、例えば、吸気圧力P1を検出する吸気圧力センサ28とともに排気圧力P2を検出する排気圧力センサを備えている場合であれば、それらのセンサ値を比較して行うものであってもよい。
Gsca=Sabyf/Iabyf×Ga
ただし、上記の式において、Sabyfは、空燃比センサ34を用いて取得される排気ガスの空燃比であり、Iabyfは、吸入空気量と燃料噴射量とに基づいて算出される目標空燃比であり、Gaは、エアフローメータ20を用いて取得される吸入空気量である。
12 燃焼室
14 吸気通路
16 排気通路
20 エアフローメータ
22 ターボ過給機
22a コンプレッサ
22b タービン
22c タービンシャフト
26 スロットルバルブ
28 吸気圧力センサ
30 燃料噴射弁
32 点火プラグ
34 空燃比センサ
36 排気バイパス通路
38 ウェイストゲートバルブ
40 触媒
42 吸気弁
44 排気弁
46 吸気可変動弁機構
48 排気可変動弁機構
50 吸気カム角センサ
52 排気カム角センサ
54 ECU(Electronic Control Unit)
Claims (2)
- 排気エネルギーにより作動するタービンを排気通路に備えるターボ過給機と、
前記タービンよりも上流側の部位において前記排気通路から分岐し、前記タービンよりも下流側の部位において前記排気通路と合流する排気バイパス通路と、
前記排気バイパス通路の開閉を切り替え可能なウェイストゲートバルブと、
排気弁の開弁期間と吸気弁の開弁期間とが重なるバルブオーバーラップ期間を変更可能とする可変動弁機構と、
燃焼室を介した吸気通路から前記排気通路への新気の吹き抜け量を取得する吹き抜け量取得手段と、
前記吹き抜け量が所定の吹き抜け判定値よりも多い場合に、当該吹き抜け量が前記吹き抜け判定値以下となるように前記バルブオーバーラップ期間を縮小させるオーバーラップ期間縮小手段と、
前記オーバーラップ期間縮小手段により前記バルブオーバーラップ期間が縮小された後に前記吹き抜け量が未だ前記吹き抜け判定値よりも多いか否かを判定する吹き抜け量判定手段と、
前記吹き抜け量判定手段により前記吹き抜け量が未だ前記吹き抜け判定値よりも多いと判定された場合に、前記ウェイストゲートバルブを開くWGV制御手段と、
を備えることを特徴とする過給機付き内燃機関の制御装置。 - 前記排気通路に配置され、排気ガスの空燃比を検出する空燃比センサを更に備え、
前記吹き抜け量取得手段は、前記空燃比センサの出力値に基づいて前記吹き抜け量を取得する手段であることを特徴とする請求項1記載の過給機付き内燃機関の制御装置。
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JP2012554516A JP5447696B2 (ja) | 2011-01-24 | 2011-01-24 | 過給機付き内燃機関の制御装置 |
PCT/JP2011/051212 WO2012101737A1 (ja) | 2011-01-24 | 2011-01-24 | 過給機付き内燃機関の制御装置 |
US13/881,084 US20130305707A1 (en) | 2011-01-24 | 2011-01-24 | Control apparatus for supercharger-equipped internal combustion engine |
EP11857005.0A EP2669497B1 (en) | 2011-01-24 | 2011-01-24 | Control device for supercharger-equipped internal combustion engine |
CN201180064542.XA CN103299050B (zh) | 2011-01-24 | 2011-01-24 | 带增压器的内燃机的控制装置 |
US14/568,190 US9470142B2 (en) | 2011-01-24 | 2014-12-12 | Control apparatus for supercharged internal combustion engine |
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PCT/JP2011/051212 WO2012101737A1 (ja) | 2011-01-24 | 2011-01-24 | 過給機付き内燃機関の制御装置 |
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US13/881,084 A-371-Of-International US20130305707A1 (en) | 2011-01-24 | 2011-01-24 | Control apparatus for supercharger-equipped internal combustion engine |
US14/568,190 Division US9470142B2 (en) | 2011-01-24 | 2014-12-12 | Control apparatus for supercharged internal combustion engine |
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EP (1) | EP2669497B1 (ja) |
JP (1) | JP5447696B2 (ja) |
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US9567886B2 (en) * | 2014-12-02 | 2017-02-14 | MAGNETI MARELLI S.p.A. | Method to control the temperature of the exhaust gases of a supercharged internal combustion engine |
JP6337819B2 (ja) * | 2015-03-30 | 2018-06-06 | トヨタ自動車株式会社 | 内燃機関 |
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EP2669497B1 (en) | 2016-01-06 |
JP5447696B2 (ja) | 2014-03-19 |
US20130305707A1 (en) | 2013-11-21 |
US9470142B2 (en) | 2016-10-18 |
EP2669497A1 (en) | 2013-12-04 |
JPWO2012101737A1 (ja) | 2014-06-30 |
CN103299050B (zh) | 2014-10-15 |
US20150096282A1 (en) | 2015-04-09 |
EP2669497A4 (en) | 2014-06-18 |
CN103299050A (zh) | 2013-09-11 |
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