JP2010138743A - Diesel engine and control method for diesel engine - Google Patents

Diesel engine and control method for diesel engine Download PDF

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JP2010138743A
JP2010138743A JP2008313996A JP2008313996A JP2010138743A JP 2010138743 A JP2010138743 A JP 2010138743A JP 2008313996 A JP2008313996 A JP 2008313996A JP 2008313996 A JP2008313996 A JP 2008313996A JP 2010138743 A JP2010138743 A JP 2010138743A
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combustion
premixed
operation region
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diesel engine
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Takero Nakajima
健朗 中島
Takahiro Ueda
隆広 植田
Yasuhiro Okubo
泰宏 大久保
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Isuzu Motors Ltd
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Abstract

<P>PROBLEM TO BE SOLVED: To provide a diesel engine and a control method for the diesel engine achieving improvement of a state of exhaust gas, improvement of fuel economy, and reduction of combustion noise of the engine due to stabilization of premixed compression ignition combustion, and expanding a premixed combustion operation area by setting compression ratio of a cylinder, an injection hole diameter of a fuel injection nozzle, and swirl ratio in a range suitable for premixed compression ignition combustion. <P>SOLUTION: In the diesel engine including a control device controlling operation with an engine operation range divided into a normal combustion operation zone V2 in which normal combustion of combustion in the cylinder of the engine is done and a premixed combustion operation zone V1 in which premixed compression ignition combustion is done, compression ratio of the cylinder is set to a range of 15.5-16.5, injection hole diameter of a fuel injection nozzle is set to a range of 0.090-0.120 mmϕ, and a variable swirl system is provided. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

本発明は、エンジンの運転領域を、エンジンのシリンダ内の燃焼で通常燃焼を行う通常燃焼運転領域と予混合圧縮着火燃焼を行う予混合燃焼運転領域とに区分して運転する制御を行う制御装置を備えたディーゼルエンジン及びディーゼルエンジンの制御方法に関する。   The present invention relates to a control device that performs control by dividing an engine operation region into a normal combustion operation region in which normal combustion is performed by combustion in a cylinder of the engine and a premixed combustion operation region in which premixed compression ignition combustion is performed. The present invention relates to a diesel engine equipped with a diesel engine and a method for controlling the diesel engine.

近年、ディーゼルエンジンにおいて、ＮＯｘとスモークの両方を同時に低減できる予混合圧縮着火燃焼の研究が活発に行われている。この予混合圧縮着火燃焼では、エンジンの軽・中負荷運転領域において、大量のＥＧＲでシリンダ内の酸素濃度を下げて、均一で希薄な低温の予混合気を生成している状態で安定した燃焼を得るために、通常燃焼に比べて、シリンダ内への燃料の噴射時期を進角させて早期噴射したり、あるいは、燃料の噴射時期を遅角させて遅延噴射したりしている。   In recent years, research on premixed compression ignition combustion that can simultaneously reduce both NOx and smoke in a diesel engine has been actively conducted. In this premixed compression ignition combustion, stable combustion is performed in a state where the oxygen concentration in the cylinder is lowered with a large amount of EGR and a uniform and lean low temperature premixed gas is generated in the light / medium load operation region of the engine. In order to achieve this, as compared with the normal combustion, the fuel injection timing into the cylinder is advanced to perform early injection, or the fuel injection timing is delayed to delay injection.

しかしながら、予混合圧縮着火燃焼をさせるために早期噴射する場合には、通常燃焼の噴射時期との間に噴射のタイミングに差が生じるため、通常燃焼と予混合圧縮着火燃焼との間での切り替えを円滑に行うことが困難となる。また、エンジン負荷が増加すると過早着火が発生し易くなり、燃料の着火時期の制御が困難となるという問題がある。この着火の制御が難しくなるとシリンダ内に噴霧された燃料を確実に燃焼することが難しくなり、燃焼が不安定となり、ＨＣやＣＯの大気中への流出が生じ易くなる。   However, in the case of early injection for premixed compression ignition combustion, there is a difference in the injection timing between the normal combustion injection timing, so switching between normal combustion and premixed compression ignition combustion It is difficult to perform smoothly. In addition, when the engine load increases, pre-ignition tends to occur, which makes it difficult to control the fuel ignition timing. If this ignition control becomes difficult, it becomes difficult to reliably burn the fuel sprayed in the cylinder, the combustion becomes unstable, and the outflow of HC and CO into the atmosphere tends to occur.

そのため、安定した燃焼を実現するためには、燃焼室における燃料の着火時期を検出する手段とこの検出した着火時期に応じた燃料噴射制御が必要となる。一般的にはこの着火時期検出手段の配置は燃焼室周辺の構造を複雑化し、また、コスト高となる。一方、予混合圧縮着火燃焼をさせるために遅延噴射する場合には、燃料の燃焼エネルギーの一部がエンジンの出力に変換されなくなるため、燃費が悪化するという問題がある。これらの問題等により、予混合圧縮着火燃焼を行うことができるエンジンの運転領域は低負荷領域に限定されている。   Therefore, in order to realize stable combustion, a means for detecting the ignition timing of the fuel in the combustion chamber and the fuel injection control according to the detected ignition timing are required. Generally, the arrangement of the ignition timing detection means complicates the structure around the combustion chamber and increases the cost. On the other hand, in the case of delayed injection for premixed compression ignition combustion, a part of the combustion energy of the fuel is not converted into the output of the engine, which causes a problem that the fuel consumption is deteriorated. Due to these problems and the like, the operating range of the engine capable of performing premixed compression ignition combustion is limited to the low load range.

これに対して、予混合燃焼運転領域の拡大のために、高温排気供給路と低温排気供給路を備え、負荷が高いほど燃焼室に供給される排気の全体量を増加させると共に低温の排気の割合を増加させる予混合圧縮着火燃焼内燃機関の燃焼制御システムや、圧縮空気噴射弁を備え、気筒内の当量比が１以上となるように予混合気を形成した後、当量比が１以下になるように圧縮空気噴射弁から気筒内に圧縮空気を直接噴射供給する予混合圧縮着火燃焼内燃機関の燃焼制御システムが提案されている（例えば、特許文献１及び２参照）。   On the other hand, in order to expand the premixed combustion operation region, a high temperature exhaust supply passage and a low temperature exhaust supply passage are provided. As the load increases, the total amount of exhaust supplied to the combustion chamber increases and the low temperature exhaust A combustion control system for a premixed compression ignition combustion internal combustion engine that increases the ratio and a compressed air injection valve are provided. After the premixed gas is formed so that the equivalent ratio in the cylinder becomes 1 or more, the equivalent ratio becomes 1 or less. A combustion control system for a premixed compression ignition combustion internal combustion engine that directly injects compressed air into a cylinder from a compressed air injection valve has been proposed (see, for example, Patent Documents 1 and 2).

また、比較的低負荷側の領域における燃焼の安定性を向上させるために、予混合圧縮着火燃焼と通常燃焼とを切替え可能とし、予混合燃焼領域において、通常燃焼領域よりもＥＧＲガス量を増加するが、低ＥＧＲ領域ではＥＧＲガス量をこの低ＥＧＲ領域以外の領域に比べて減少し、吸気量低減領域では吸気量を減少する予混合圧縮着火内燃機関が提案されている（例えば、特許文献３参照）。   In addition, in order to improve the stability of combustion in the relatively low load region, it is possible to switch between premixed compression ignition combustion and normal combustion, and in the premixed combustion region, the amount of EGR gas is increased compared to the normal combustion region. However, a premixed compression ignition internal combustion engine has been proposed in which the EGR gas amount is reduced in the low EGR region as compared to regions other than the low EGR region, and the intake amount is reduced in the intake amount reduction region (for example, Patent Documents). 3).

しかしながら、上記の構成では、エンジンの構造が複雑化したり、予混合燃焼運転領域の拡大が不十分であったりするという問題がある。
特開２００５−３６６５５公報 特開２００５−３２５７４８公報 特開２００８−１９０４３２公報 However, the above configuration has a problem that the structure of the engine is complicated and the premixed combustion operation region is not sufficiently expanded.
JP 2005-36655 A JP 2005-325748 A JP 2008-190432 A

本発明は、上記の状況を鑑みてなされたものであり、その目的は、エンジンの運転領域を、エンジンのシリンダ内の燃焼で通常燃焼を行う通常燃焼運転領域と予混合圧縮着火燃焼を行う予混合燃焼運転領域とに区分して運転する制御を行う制御装置を備えたディーゼルエンジンにおいて、シリンダの圧縮比、燃料噴射ノズルの噴孔径、スワール比を予混合圧縮着火燃焼に適した範囲に設定することにより、予混合圧縮着火燃焼の安定化により、排気ガスの状態の良好化と、燃費の改善と、エンジンの燃焼音の低減を図ることができ、予混合燃焼運転領域を拡大できるディーゼルエンジン及びディーゼルエンジンの制御方法を提供することにある。   The present invention has been made in view of the above situation, and an object of the present invention is to divide the engine operation region into a normal combustion operation region in which normal combustion is performed by combustion in a cylinder of the engine and a premixed compression ignition combustion. In a diesel engine equipped with a control device that performs control by dividing into a mixed combustion operation region, the cylinder compression ratio, the nozzle hole diameter of the fuel injection nozzle, and the swirl ratio are set to a range suitable for premixed compression ignition combustion. Thus, by stabilizing the premixed compression ignition combustion, it is possible to improve the exhaust gas state, improve the fuel consumption, reduce the combustion noise of the engine, and expand the premixed combustion operation range. It is in providing the control method of a diesel engine.

上記の目的を達成するための本発明のディーゼルエンジンは、エンジンの運転領域を、エンジンのシリンダ内の燃焼で通常燃焼を行う通常燃焼運転領域と予混合圧縮着火燃焼を行う予混合燃焼運転領域とに区分して運転する制御を行う制御装置を備えたディーゼルエンジンにおいて、シリンダの圧縮比を１５．５〜１６．５とし、燃料噴射ノズルの噴孔径を０．０９０ｍｍφ〜０．１２０ｍｍφとすると共に、スワール可変システムを備えて構成する。   In order to achieve the above object, the diesel engine of the present invention includes an engine operating region, a normal combustion operating region in which normal combustion is performed by combustion in a cylinder of the engine, and a premixed combustion operating region in which premixed compression ignition combustion is performed. In a diesel engine equipped with a control device that performs control to be divided into two types, a cylinder compression ratio is set to 15.5 to 16.5, a nozzle hole diameter of a fuel injection nozzle is set to 0.090 mmφ to 0.120 mmφ, Configure with a swirl variable system.

この構成により、予混合圧縮着火燃焼の安定化することができるので、排気ガスのエミッションや燃費や燃焼音を低減しながら、予混合燃焼運転領域を広げることができるようになる。また、着火時期検出手段が不要となる。   With this configuration, premixed compression ignition combustion can be stabilized, so that the premixed combustion operation region can be expanded while reducing exhaust gas emission, fuel consumption, and combustion noise. Further, the ignition timing detection means is not necessary.

上記のディーゼルエンジンにおいて、前記制御装置が、前記予混合燃焼運転領域では、前記通常燃焼運転領域よりも、ＥＧＲ率を増加し、空気過剰率λを低くし、スワール比を高くし、燃料噴射圧を増加して、予混合圧縮着火燃焼を行う制御をするように構成する。言い換えれば、予混合燃焼運転領域では、通常燃焼運転領域よりも、吸入空気量を低減して空気過剰率λを予め設定した範囲とし、燃料噴射の間はスワール可変システム（ＶＳＳ）によりスワール比を高め、ＥＧＲ率を増加する制御を行う。また、燃料噴射圧力を高めて通常燃焼より高圧で噴射させる。この高圧噴射では、燃料噴射システムをコモンレール燃料噴射システムで形成することが好ましい。   In the diesel engine, the control device increases the EGR rate, lowers the excess air ratio λ, increases the swirl ratio, and increases the fuel injection pressure in the premixed combustion operation region than in the normal combustion operation region. Is controlled so as to perform premixed compression ignition combustion. In other words, in the premixed combustion operation region, the intake air amount is reduced and the excess air ratio λ is set in a preset range compared to the normal combustion operation region, and the swirl ratio is set by the swirl variable system (VSS) during fuel injection. Control to increase and increase the EGR rate. Further, the fuel injection pressure is increased and the fuel is injected at a pressure higher than that of normal combustion. In this high pressure injection, the fuel injection system is preferably formed by a common rail fuel injection system.

この構成により、より安定した予混合圧縮着火燃焼を行うことができる。また、メイン噴射の噴射時期を、通常燃焼運転領域と同様の噴射時期で予混合圧縮着火燃焼をすることができるようになる。   With this configuration, more stable premixed compression ignition combustion can be performed. Further, the premixed compression ignition combustion can be performed at the injection timing of the main injection at the same injection timing as in the normal combustion operation region.

上記のディーゼルエンジンにおいて、前記制御装置が、前記予混合燃焼運転領域では、メイン噴射時期を上死点前とし、このメイン噴射後の０．１ｍｓ〜０．５ｍｓの範囲内でアフター噴射する制御をするように構成する。なお、この安定した近接噴射、即ち、メイン噴射後からのインターバルを短縮した噴射を得るためには、燃料噴射システムを、ピエゾ方式のコモンレール燃料噴射システムとすることが好ましい。   In the diesel engine, in the premixed combustion operation region, the control device controls the main injection timing to be before top dead center and after-injection within a range of 0.1 ms to 0.5 ms after the main injection. To be configured. In order to obtain this stable proximity injection, that is, injection with a reduced interval after the main injection, the fuel injection system is preferably a piezo-type common rail fuel injection system.

この構成によれば、予混合燃焼運転領域におけるメイン噴射時期が通常燃焼運転領域におけるメイン噴射時期と同じになるので、予混合燃焼運転領域と通常燃焼運転領域との間の切替えを円滑に行うことができるようになる。また、多量ＥＧＲ状態下では燃料噴射の後半において酸素が十分に供給され難くなる噴霧中心軸付近において、燃料噴射量をメイン噴射とアフター噴射とで分割し、アフター噴射を行うことで、空気を取り込み易くする。これにより、噴霧された燃料を燃焼し易くして、不完全燃焼に起因するスモークを低減することができる。   According to this configuration, since the main injection timing in the premixed combustion operation region is the same as the main injection timing in the normal combustion operation region, the switching between the premixed combustion operation region and the normal combustion operation region can be performed smoothly. Will be able to. Also, in the vicinity of the spray center axis where oxygen is difficult to be sufficiently supplied in the second half of fuel injection under a large amount of EGR, the fuel injection amount is divided into main injection and after injection, and after-injection is performed to capture air. Make it easier. Thereby, the sprayed fuel can be easily burned, and smoke caused by incomplete combustion can be reduced.

上記のディーゼルエンジンにおいて、ピストン燃焼室口元径をボア比で０・５８〜０．６８とすると、シリンダの圧縮比において容易に低圧縮比を得ることできるようになる。   In the diesel engine described above, when the piston combustion chamber mouth diameter is set to 0.58 to 0.68 in terms of bore ratio, a low compression ratio can be easily obtained in the cylinder compression ratio.

そして、上記の目的を達成するための本発明のディーゼルエンジンの制御方法は、エンジンの運転領域を、エンジンのシリンダ内の燃焼で通常燃焼を行う通常燃焼運転領域と予混合圧縮着火燃焼を行う予混合燃焼運転領域とに区分して運転する制御を行う制御装置を備えると共に、シリンダの圧縮比を１５．５〜１６．５とし、燃料噴射ノズルの噴孔径を０．０９０ｍｍφ〜０．１２０ｍｍφとして、スワール可変システムを備えたディーゼルエンジンの制御方法において、前記予混合燃焼運転領域では、前記通常燃焼運転領域よりも、ＥＧＲ率を増加し、空気過剰率λを低くし、スワール比を高くし、燃料噴射圧を増加して、予混合圧縮着火燃焼を行うことを特徴とする制御方法である。   The method for controlling a diesel engine of the present invention for achieving the above object includes a normal combustion operation region in which normal combustion is performed by combustion in a cylinder of the engine and a premixed compression ignition combustion in which the engine is operated. A control device that performs control to be divided into the mixed combustion operation region is provided, the cylinder compression ratio is set to 15.5 to 16.5, and the nozzle diameter of the fuel injection nozzle is set to 0.090 mmφ to 0.120 mmφ. In the control method of the diesel engine provided with the swirl variable system, in the premixed combustion operation region, the EGR rate is increased, the excess air ratio λ is decreased, the swirl ratio is increased, and the fuel is increased. The control method is characterized in that the injection pressure is increased and premixed compression ignition combustion is performed.

この制御方法により、予混合圧縮着火燃焼の安定化することができるので、排気ガスのエミッションや燃費や燃焼音を低減しながら、予混合燃焼運転領域を広げることができるようになる。また、着火時期検出手段が不要となる。更に、メインの噴射時期を、通常燃焼運転領域と同様の噴射時期で予混合圧縮着火燃焼をすることができるようになる。   With this control method, premixed compression ignition combustion can be stabilized, so that the premixed combustion operation region can be expanded while reducing exhaust gas emission, fuel consumption, and combustion noise. Further, the ignition timing detection means is not necessary. Furthermore, premixed compression ignition combustion can be performed at the main injection timing at the same injection timing as in the normal combustion operation region.

上記のディーゼルエンジンの制御方法において、前記予混合燃焼運転領域では、メイン噴射時期を上死点前とし、このメイン噴射後の０．１ｍｓ〜０．５ｍｓの範囲内でアフター噴射すると、予混合燃焼運転領域におけるメイン噴射時期が通常燃焼運転領域におけるメイン噴射時期と同じになるので、予混合燃焼運転領域と通常燃焼運転領域との間の切替えを円滑に行うことができるようになる。また、スモークを低減することができる。   In the diesel engine control method described above, in the premixed combustion operation region, when the main injection timing is set at the top dead center and after injection is performed within a range of 0.1 ms to 0.5 ms after the main injection, the premixed combustion is performed. Since the main injection timing in the operation region is the same as the main injection timing in the normal combustion operation region, switching between the premixed combustion operation region and the normal combustion operation region can be performed smoothly. Also, smoke can be reduced.

更に、上記のディーゼルエンジンの制御方法において、前記予混合燃焼運転領域であるか否かを、吸引空気量と、燃料流量と、メイン噴射時期と、エンジン水温と、エンジン回転速度とをそれぞれの予め設定した値と比較して判定すると、これにより、予混合圧縮着火燃焼に移行するタイミングを的確に判定することができるようになる。   Further, in the above diesel engine control method, whether or not it is the premixed combustion operation region is determined based on the intake air amount, the fuel flow rate, the main injection timing, the engine water temperature, and the engine rotation speed in advance. When the determination is made in comparison with the set value, the timing for shifting to the premixed compression ignition combustion can be accurately determined.

本発明に係るディーゼルエンジンによれば、エンジンの運転領域を、エンジンのシリンダ内の燃焼で通常燃焼を行う通常燃焼運転領域と予混合圧縮着火燃焼を行う予混合燃焼運転領域とに区分して運転する制御を行う制御装置を備えたディーゼルエンジンにおいて、シリンダの圧縮比、燃料噴射ノズルの噴孔径、スワール比を予混合圧縮着火燃焼に適した範囲に設定することにより、より広いエンジンの運転領域で予混合圧縮着火燃焼を安定化することができるようになり、排気ガスの状態の良好化と、燃費の改善と、エンジンの燃焼音の低減を図ることができる。従って、エンジンの運転領域における予混合燃焼運転領域を拡大できる。   According to the diesel engine according to the present invention, the engine operation region is divided into a normal combustion operation region in which normal combustion is performed by combustion in the cylinder of the engine and a premixed combustion operation region in which premixed compression ignition combustion is performed. In a diesel engine equipped with a control device that performs control, the cylinder compression ratio, the nozzle hole diameter of the fuel injection nozzle, and the swirl ratio are set in a range suitable for premixed compression ignition combustion, thereby enabling a wider engine operating range. Premixed compression ignition combustion can be stabilized, and the state of exhaust gas can be improved, the fuel consumption can be improved, and the combustion noise of the engine can be reduced. Therefore, the premixed combustion operation region in the engine operation region can be expanded.

更に、予混合燃焼運転領域で、通常燃焼運転領域よりも、空気過剰率λを低くし、スワール比を高くし、ＥＧＲ率を増加し、燃料噴射圧を増加して、予混合圧縮着火燃焼を行うことにより、メイン噴射の噴射時期を、通常燃焼運転領域と同様の噴射時期で予混合圧縮着火燃焼をすることができるようになる。従って、予混合燃焼運転領域と通常燃焼運転領域との間での円滑な切替えを行うことができるようになる。   Further, in the premixed combustion operation region, the excess air ratio λ is lowered, the swirl ratio is increased, the EGR rate is increased, the fuel injection pressure is increased, and the premixed compression ignition combustion is performed. By doing so, the premixed compression ignition combustion can be performed at the injection timing of the main injection at the same injection timing as in the normal combustion operation region. Therefore, smooth switching between the premixed combustion operation region and the normal combustion operation region can be performed.

以下、本発明に係る実施の形態のディーゼルエンジン及びディーゼルエンジンの制御方法について、図面を参照しながら説明する。   Hereinafter, a diesel engine and a diesel engine control method according to embodiments of the present invention will be described with reference to the drawings.

本発明に係る実施の形態のディーゼルエンジンでは、ＥＣＵ（エンジンコントロールユニット）と呼ばれる制御装置により、エンジンの運転領域を、エンジンのシリンダ内の燃焼で通常燃焼を行う通常燃焼運転領域と予混合圧縮着火燃焼を行う予混合燃焼運転領域とに区分して運転する制御を行う。この両運転領域の区分は、吸引空気量と、燃料流量と、メイン噴射時期と、エンジン水温と、エンジン回転速度とをそれぞれの予め設定した値と比較して判定する。これにより、予混合圧縮着火燃焼Ｖ１に移行するタイミングを的確に判定することができるようになる。   In a diesel engine according to an embodiment of the present invention, a control device called an ECU (engine control unit) controls an engine operating region, a normal combustion operating region in which normal combustion is performed by combustion in an engine cylinder, and premixed compression ignition. Control is performed by dividing into a premixed combustion operation region in which combustion is performed. The classification of the two operation regions is determined by comparing the intake air amount, the fuel flow rate, the main injection timing, the engine water temperature, and the engine rotation speed with respective preset values. This makes it possible to accurately determine the timing for shifting to the premixed compression ignition combustion V1.

図１にこの両運転領域を模式的に示す。図１では、横軸をエンジン回転数で、縦軸を燃料流量（負荷）で、２次元的に、予混合燃焼運転領域Ｖ１と通常燃焼運転領域Ｖ２とを示してあるが、実際には、更に、吸引空気量とメイン噴射時期とエンジン水温も考慮して、エンジンの運転領域を通常燃焼運転領域と予混合燃焼運転領域のいずれかにあると判定する。ここでは、燃料流量（負荷）が比較的小さい軽・中負荷運転領域が、予混合燃焼運転領域Ｖ１となる。この予混合燃焼運転領域Ｖ１では、多量のＥＧＲで、低酸素状態で燃焼が行われる。   FIG. 1 schematically shows both operating regions. In FIG. 1, the horizontal axis indicates the engine speed, the vertical axis indicates the fuel flow rate (load), and the two-dimensional premixed combustion operation region V1 and the normal combustion operation region V2 are shown. Further, in consideration of the intake air amount, the main injection timing, and the engine water temperature, it is determined that the engine operation region is in either the normal combustion operation region or the premixed combustion operation region. Here, the light / medium load operation region where the fuel flow rate (load) is relatively small is the premixed combustion operation region V1. In the premixed combustion operation region V1, combustion is performed in a low oxygen state with a large amount of EGR.

本発明においては、より広いエンジンの運転領域で予混合圧縮着火燃焼を安定して行えるようにして、予混合燃焼運転領域Ｖ１を広げるために、ディーゼルエンジンを、シリンダの圧縮比を１５．５〜１６．５とし、燃料噴射ノズルの噴孔径を０．０９０ｍｍφ〜０．１２０ｍｍφとする。また、それと共に、スワール可変システムを備えて構成する。また、このシリンダの低圧縮比に関しては、ピストン燃焼室口元径をボア比で０・５８〜０．６８とすると、容易に低圧縮比を得ることができるようになる。   In the present invention, in order to expand the premixed combustion operation region V1 so that the premixed compression ignition combustion can be stably performed in a wider engine operation region, the compression ratio of the cylinder is set to 15.5. 16.5, and the nozzle diameter of the fuel injection nozzle is 0.090 mmφ to 0.120 mmφ. Along with that, a swirl variable system is provided. Further, regarding the low compression ratio of this cylinder, it is possible to easily obtain a low compression ratio by setting the piston combustion chamber mouth diameter to 0.55 to 0.68 in terms of bore ratio.

シリンダの圧縮比を１５．５より小さくすると、低温始動性の悪化、ＨＣとＣＯの排出量の増加という問題があり、１６．５より大きくすると、圧縮機の温度が上昇し、予混合燃焼運転領域が狭くなり、また、部分負荷域におけるＮＯｘ−ＰＭのトレードオフが悪化するという問題がある。また、燃料噴射ノズルの噴孔径を、０．０９０ｍｍφより小さくすると目詰まりし易くなるというという問題があり、０．１２０ｍｍφより大きくすると、噴霧状況が悪くなる問題がある。また、ピストン燃焼室口元径をボア比で０・５８より小さくすると燃料噴霧が燃焼室の壁面に衝突し易くなるという問題と燃焼室が深くなり混合気の形成が悪化するという問題があり、０．６８より大きくすると、燃焼室口元の機械や、熱応力の合成応力が大きくなる等構造上の制約があるという問題がある。   If the compression ratio of the cylinder is smaller than 15.5, there is a problem that the cold startability is deteriorated and the amount of HC and CO emissions is increased. If the compression ratio is larger than 16.5, the temperature of the compressor rises and premixed combustion operation is performed. There is a problem that the region becomes narrow and the NOx-PM trade-off in the partial load region deteriorates. Further, there is a problem that if the nozzle diameter of the fuel injection nozzle is smaller than 0.090 mmφ, clogging is likely to occur, and if it is larger than 0.120 mmφ, there is a problem that the spraying condition becomes worse. Further, if the piston combustion chamber opening diameter is smaller than 0 · 58 by the bore ratio, there is a problem that the fuel spray easily collides with the wall surface of the combustion chamber and a problem that the combustion chamber becomes deep and the mixture formation is deteriorated. If it is larger than .68, there is a problem that there are structural restrictions such as the machine at the mouth of the combustion chamber and the combined stress of thermal stress becomes large.

このディーゼルエンジンにおいては、シリンダ内への燃料噴射制御で高圧噴射を行うために、燃料噴射システムをコモンレール燃料噴射システムで形成することが好ましく、更に、メイン噴射に近接したアフター噴射で、安定した近接噴射を得るためには、ピエゾ方式のコモンレール燃料噴射システムとすることが好ましい。   In this diesel engine, in order to perform high-pressure injection by controlling fuel injection into the cylinder, it is preferable that the fuel injection system is formed by a common rail fuel injection system. In order to obtain injection, it is preferable to use a piezo-type common rail fuel injection system.

次に、上記の構成のディーゼルエンジンにおける制御方法について説明する。このエンジンの制御方法においては、吸引空気量が予め設定した空気量閾値以下で、燃料流量が予め設定した燃料流量閾値以下で、メイン噴射時期が予め設定した範囲内で、エンジン水温が予め設定したエンジン水温閾値以下で、エンジン回転速度が予め設定したエンジン回転速度閾値以下の場合に、エンジンの運転領域が予混合燃焼運転領域Ｖ１にあると判定する。   Next, a control method in the diesel engine having the above configuration will be described. In this engine control method, the engine water temperature is preset within a range in which the intake air amount is less than or equal to a preset air amount threshold, the fuel flow rate is less than or equal to a preset fuel flow rate threshold, and the main injection timing is preset. When the engine speed is equal to or lower than the engine water temperature threshold and the engine speed is equal to or lower than a preset engine speed threshold, it is determined that the engine operating range is in the premixed combustion operating range V1.

エンジンの運転領域が、予め設定した予混合燃焼運転領域Ｖ１あると判定されると、図２に示すように、この予混合燃焼運転領域Ｖ１では、通常燃焼運転領域Ｖ２よりも、空気過剰率λを低くし、スワール比を高くし、ＥＧＲ率を増加し、燃料噴射圧を増加して、予混合圧縮着火燃焼を行う制御する。つまり、予混合燃焼運転領域Ｖ１では、通常燃焼運転領域Ｖ２よりも、吸入空気量を低減して空気過剰率λを予め設定した範囲とし、燃料噴射の間はスワール可変システム（ＶＳＳ）によりスワール比を高め、ＥＧＲ率を増加する制御を行う。また、燃料噴射圧力を高めて通常燃焼より高圧で噴射させる。この高圧噴射により、燃料の噴射期間を短縮し、この噴射時間の短縮により、吸入空気と燃料の混合期間の長期化を行う。   If it is determined that the engine operating range is the preset premixed combustion operating range V1, as shown in FIG. 2, the premixed combustion operating range V1 has an excess air ratio λ as compared with the normal combustion operating range V2. Is controlled, the swirl ratio is increased, the EGR rate is increased, the fuel injection pressure is increased, and the premixed compression ignition combustion is performed. That is, in the premixed combustion operation region V1, the intake air amount is reduced and the excess air ratio λ is set in a predetermined range compared to the normal combustion operation region V2, and the swirl ratio is set by the swirl variable system (VSS) during fuel injection. To increase the EGR rate. Further, the fuel injection pressure is increased and the fuel is injected at a pressure higher than that of normal combustion. By this high pressure injection, the fuel injection period is shortened, and by shortening the injection time, the intake air and fuel mixing period is lengthened.

より具体的には、２段過給システムのエンジンの例ではあるが、例えば、１５００ｒｐｍ／４０Ｎｍ条件下の予混合燃焼運転領域Ｖ１では、空気過剰率λを１．１０〜１．４５とし、スワール比を２．０〜２．７とし、ＥＧＲ率を５０％〜６０％とし、燃料噴射圧を５５ＭＰａ〜９０ＭＰａとして、予混合圧縮着火燃焼を行う制御をする。   More specifically, although it is an example of the engine of the two-stage supercharging system, for example, in the premixed combustion operation region V1 under the condition of 1500 rpm / 40 Nm, the excess air ratio λ is set to 1.10 to 1.45, and the swirl The ratio is set to 2.0 to 2.7, the EGR rate is set to 50% to 60%, the fuel injection pressure is set to 55 MPa to 90 MPa, and premixed compression ignition combustion is controlled.

空気過剰率λを１．４５より小さくすることにより、予混合圧縮着火燃焼に適した酸素濃度に低下させることができるが、１．１０よりも小さいと酸素不足になって燃焼が悪化する。スワール比を２．０より小さくすると燃料と吸入空気との混合効果が薄れ、２．７より大きくしようとするとポートの有効面積が減り、燃費が悪化する。また、ＥＧＲ率が５０％より小さいとＥＧＲ効果が薄れ、低温で低ＮＯｘ燃焼を行えなくなり、６０％以上であると酸素不足となり燃焼が悪化する。燃料噴射圧を５５ＭＰａより小さくすると噴霧状態が不十分となり燃料と吸入空気との混合効果が薄れ、９０ＭＰａより大きくしようとすると燃費の悪化と燃焼音の悪化を招くことになる。   By making the excess air ratio λ smaller than 1.45, it is possible to lower the oxygen concentration suitable for premixed compression ignition combustion, but when it is smaller than 1.10, the oxygen becomes insufficient and the combustion deteriorates. If the swirl ratio is less than 2.0, the mixing effect of the fuel and the intake air is weakened. If the swirl ratio is made larger than 2.7, the effective area of the port is reduced and the fuel consumption is deteriorated. Further, if the EGR rate is less than 50%, the EGR effect is weakened, and low NOx combustion cannot be performed at a low temperature, and if it is 60% or more, oxygen is insufficient and combustion deteriorates. If the fuel injection pressure is less than 55 MPa, the spray state becomes insufficient and the mixing effect of the fuel and the intake air is reduced, and if it exceeds 90 MPa, the fuel consumption and the combustion noise are deteriorated.

また、燃料噴射制御に関しては、予混合燃焼運転領域Ｖ１では、メイン噴射時期を、通常燃焼運転領域におけるメイン噴射時期と同じ、即ち、上死点前とし、このメイン噴射後の直後、即ち、０．１ｍｓ〜０．５ｍｓの範囲でアフター噴射する制御を行う。   Regarding fuel injection control, in the premixed combustion operation region V1, the main injection timing is the same as the main injection timing in the normal combustion operation region, that is, before top dead center, and immediately after this main injection, that is, 0. .After-injection control is performed in the range of 1 ms to 0.5 ms.

このアフター噴射を行うことで、燃料噴射量をメイン噴射とアフター噴射とで分割し、多量ＥＧＲ状態下では燃料噴射の後半において酸素が十分に供給され難くなる噴霧中心軸付近における空気の取り込みを容易とする。これにより、噴霧された燃料を燃焼し易くして、不完全燃焼に起因するスモークを低減することができる。   By performing this after-injection, the fuel injection amount is divided into main injection and after-injection, and in a large amount of EGR, it is easy to take in air in the vicinity of the spray center axis where oxygen is not sufficiently supplied in the second half of fuel injection And Thereby, the sprayed fuel can be easily burned, and smoke caused by incomplete combustion can be reduced.

上記のディーゼルエンジン及びディーゼルエンジンの制御方法によれば、予混合圧縮着火燃焼の安定化することができるので、排気ガスのエミッションや燃費や燃焼音を低減しながら、予混合燃焼運転領域を広げることができるようになる。また、着火時期検出手段が不要となる。   According to the above diesel engine and diesel engine control method, premixed compression ignition combustion can be stabilized, so that the premixed combustion operation range can be expanded while reducing exhaust gas emission, fuel consumption and combustion noise. Will be able to. Further, the ignition timing detection means is not necessary.

また、メイン噴射の噴射時期を、通常燃焼運転領域と同様の噴射時期で予混合圧縮着火燃焼をすることができるようになる。その結果、予混合燃焼運転領域におけるメイン噴射時期が通常燃焼運転領域におけるメイン噴射時期と同じになるので、予混合燃焼運転領域と通常燃焼運転領域との切替えを円滑に行うことができるようになる。   Further, the premixed compression ignition combustion can be performed at the injection timing of the main injection at the same injection timing as in the normal combustion operation region. As a result, the main injection timing in the premixed combustion operation region becomes the same as the main injection timing in the normal combustion operation region, so that the switching between the premixed combustion operation region and the normal combustion operation region can be performed smoothly. .

本発明に係る実施の形態のディーゼルエンジンにおけるの予混合燃焼領域と通常燃焼領域を模式的に示す図である。It is a figure which shows typically the premixed combustion area | region and normal combustion area | region in the diesel engine of embodiment which concerns on this invention. 本発明に係る実施の形態のディーゼルエンジンの予混合燃焼領域と通常燃焼領域のそれぞれの制御モードの制御量の状態を模式的に示す図である。It is a figure which shows typically the state of the controlled variable of each control mode of the pre-mixing combustion area | region of a diesel engine of embodiment which concerns on this invention, and a normal combustion area | region.

符号の説明Explanation of symbols

Ｖ１ 予混合燃焼領域
Ｖ２ 通常燃焼領域 V1 Premixed combustion region V2 Normal combustion region

Claims (7)

エンジンの運転領域を、エンジンのシリンダ内の燃焼で通常燃焼を行う通常燃焼運転領域と予混合圧縮着火燃焼を行う予混合燃焼運転領域とに区分して運転する制御を行う制御装置を備えたディーゼルエンジンにおいて、
シリンダの圧縮比を１５．５〜１６．５とし、燃料噴射ノズルの噴孔径を０．０９０ｍｍφ〜０．１２０ｍｍφとすると共に、スワール可変システムを備えたことを特徴とするディーゼルエンジン。 Diesel equipped with a control device that performs control to divide the engine operation region into a normal combustion operation region where normal combustion is performed by combustion in the cylinder of the engine and a premixed combustion operation region where premixed compression ignition combustion is performed In the engine,
A diesel engine having a cylinder compression ratio of 15.5 to 16.5, a nozzle diameter of a fuel injection nozzle of 0.090 mmφ to 0.120 mmφ, and a swirl variable system. 前記制御装置が、前記予混合燃焼運転領域では、前記通常燃焼運転領域よりも、ＥＧＲ率を増加し、空気過剰率λを低くし、スワール比を高くし、燃料噴射圧を増加して、予混合圧縮着火燃焼を行う制御をすることを特徴とする請求項１に記載のディーゼルエンジン。   In the premixed combustion operation region, the control device increases the EGR rate, lowers the excess air ratio λ, increases the swirl ratio, increases the fuel injection pressure, and increases the fuel injection pressure. 2. The diesel engine according to claim 1, wherein control for performing mixed compression ignition combustion is performed. 3. 前記制御装置が、前記予混合燃焼運転領域では、メイン噴射時期を上死点前とし、このメイン噴射後の０．１ｍｓ〜０．５ｍｓの範囲内でアフター噴射する制御をすることを特徴とする請求項１又は２に記載のディーゼルエンジン。   In the premixed combustion operation region, the control device controls the main injection timing to be before top dead center and performs after injection within a range of 0.1 ms to 0.5 ms after the main injection. The diesel engine according to claim 1 or 2. ピストン燃焼室口元径をボア比で０・５８〜０．６８とすることを特徴とする請求項１、２、又は３に記載のディーゼルエンジン。   The diesel engine according to claim 1, 2, or 3, wherein the piston combustion chamber has a bore diameter of 0.58 to 0.68 in terms of bore ratio. エンジンの運転領域を、エンジンのシリンダ内の燃焼で通常燃焼を行う通常燃焼運転領域と予混合圧縮着火燃焼を行う予混合燃焼運転領域とに区分して運転する制御を行う制御装置を備えると共に、シリンダの圧縮比を１５．５〜１６．５とし、燃料噴射ノズルの噴孔径を０．０９０ｍｍφ〜０．１２０ｍｍφとして、スワール可変システムを備えたディーゼルエンジンの制御方法において、
前記予混合燃焼運転領域では、前記通常燃焼運転領域よりも、ＥＧＲ率を増加し、空気過剰率λを低くし、スワール比を高くし、燃料噴射圧を増加して、予混合圧縮着火燃焼を行うことを特徴とするディーゼルエンジンの制御方法。 A control device that performs control to divide the engine operation region into a normal combustion operation region in which normal combustion is performed by combustion in a cylinder of the engine and a premixed combustion operation region in which premixed compression ignition combustion is performed; In a method for controlling a diesel engine equipped with a swirl variable system, the compression ratio of the cylinder is 15.5 to 16.5, the nozzle diameter of the fuel injection nozzle is 0.090 mmφ to 0.120 mmφ,
In the premixed combustion operation region, the EGR rate is increased, the excess air ratio λ is decreased, the swirl ratio is increased, the fuel injection pressure is increased, and the premixed compression ignition combustion is performed. A method for controlling a diesel engine, comprising: 前記予混合燃焼運転領域では、メイン噴射時期を上死点前とし、このメイン噴射後の０．１ｍｓ〜０．５ｍｓの範囲内でアフター噴射することを特徴とする請求項５に記載のディーゼルエンジンの制御方法。   6. The diesel engine according to claim 5, wherein in the premixed combustion operation region, the main injection timing is set to before the top dead center, and after injection is performed within a range of 0.1 ms to 0.5 ms after the main injection. Control method. 前記予混合燃焼運転領域であるか否かを、吸引空気量と、燃料流量と、メイン噴射時期と、エンジン水温と、エンジン回転速度とをそれぞれの予め設定した値と比較して判定することを特徴とする請求項５、又は６に記載のディーゼルエンジンの制御方法。   It is determined whether the premixed combustion operation region is in comparison with the intake air amount, the fuel flow rate, the main injection timing, the engine water temperature, and the engine rotational speed with respective preset values. The method for controlling a diesel engine according to claim 5 or 6, characterized by the above.
JP2008313996A 2008-12-10 2008-12-10 Diesel engine and control method for diesel engine Pending JP2010138743A (en)

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Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2012098671A1 (en) * 2011-01-20 2012-07-26 トヨタ自動車株式会社 Control device for internal combustion engine
JP2013096271A (en) * 2011-10-31 2013-05-20 Isuzu Motors Ltd Internal combustion engine using liquefied gas as fuel
JP2019039359A (en) * 2017-08-25 2019-03-14 マツダ株式会社 Fuel injection device for engine
JP2019194458A (en) * 2018-05-02 2019-11-07 マツダ株式会社 Control device for compression ignition type engine
JP2019194459A (en) * 2018-05-02 2019-11-07 マツダ株式会社 Control device for compression ignition engine
US11220972B2 (en) 2018-05-02 2022-01-11 Mazda Motor Corporation Control apparatus for compression-ignition type engine
US11326543B2 (en) 2018-05-02 2022-05-10 Mazda Motor Corporation Control apparatus for compression-ignition type engine

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH09228838A (en) * 1996-02-26 1997-09-02 Shin A C Ii:Kk Direct injection type diesel engine
JP2000274286A (en) * 1999-03-19 2000-10-03 Nissan Motor Co Ltd Direct injection type diesel engine
JP2002180881A (en) * 2000-12-08 2002-06-26 Mazda Motor Corp Combustion controller for diesel engine
JP2003286886A (en) * 2002-03-28 2003-10-10 Mazda Motor Corp Combustion controller for diesel engine
JP2004100557A (en) * 2002-09-09 2004-04-02 Toyota Motor Corp Fuel injection control device of internal combustion engine
JP2005155603A (en) * 2003-11-04 2005-06-16 Denso Corp Internal combustion engine
JP2006029292A (en) * 2004-07-21 2006-02-02 Toyota Motor Corp Reentrant type combustion chamber of direct-injection compression ignition engine, and direct-injection compression ignition engine
JP2006105046A (en) * 2004-10-06 2006-04-20 Isuzu Motors Ltd Control device of diesel engine

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH09228838A (en) * 1996-02-26 1997-09-02 Shin A C Ii:Kk Direct injection type diesel engine
JP2000274286A (en) * 1999-03-19 2000-10-03 Nissan Motor Co Ltd Direct injection type diesel engine
JP2002180881A (en) * 2000-12-08 2002-06-26 Mazda Motor Corp Combustion controller for diesel engine
JP2003286886A (en) * 2002-03-28 2003-10-10 Mazda Motor Corp Combustion controller for diesel engine
JP2004100557A (en) * 2002-09-09 2004-04-02 Toyota Motor Corp Fuel injection control device of internal combustion engine
JP2005155603A (en) * 2003-11-04 2005-06-16 Denso Corp Internal combustion engine
JP2006029292A (en) * 2004-07-21 2006-02-02 Toyota Motor Corp Reentrant type combustion chamber of direct-injection compression ignition engine, and direct-injection compression ignition engine
JP2006105046A (en) * 2004-10-06 2006-04-20 Isuzu Motors Ltd Control device of diesel engine

Cited By (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2012098671A1 (en) * 2011-01-20 2012-07-26 トヨタ自動車株式会社 Control device for internal combustion engine
CN103328792A (en) * 2011-01-20 2013-09-25 丰田自动车株式会社 Control device for internal combustion engine
JP5556906B2 (en) * 2011-01-20 2014-07-23 トヨタ自動車株式会社 Control device for internal combustion engine
CN103328792B (en) * 2011-01-20 2015-01-14 丰田自动车株式会社 Control device for internal combustion engine
US9051894B2 (en) 2011-01-20 2015-06-09 Toyota Jidosha Kabushiki Kaisha Control device for internal combustion engine
JP2013096271A (en) * 2011-10-31 2013-05-20 Isuzu Motors Ltd Internal combustion engine using liquefied gas as fuel
JP2019039359A (en) * 2017-08-25 2019-03-14 マツダ株式会社 Fuel injection device for engine
JP2019194458A (en) * 2018-05-02 2019-11-07 マツダ株式会社 Control device for compression ignition type engine
JP2019194459A (en) * 2018-05-02 2019-11-07 マツダ株式会社 Control device for compression ignition engine
US11203969B2 (en) 2018-05-02 2021-12-21 Mazda Motor Corporation Control apparatus for compression-ignition type engine
US11220972B2 (en) 2018-05-02 2022-01-11 Mazda Motor Corporation Control apparatus for compression-ignition type engine
US11220971B2 (en) 2018-05-02 2022-01-11 Mazda Motor Corporation Control apparatus for compression-ignition type engine
JP7047581B2 (en) 2018-05-02 2022-04-05 マツダ株式会社 Compression ignition engine controller
JP7047580B2 (en) 2018-05-02 2022-04-05 マツダ株式会社 Compression ignition engine controller
US11326543B2 (en) 2018-05-02 2022-05-10 Mazda Motor Corporation Control apparatus for compression-ignition type engine

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