CN102322360B - In-cylinder direction injection gasoline engine and control method thereof - Google Patents
In-cylinder direction injection gasoline engine and control method thereof Download PDFInfo
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- CN102322360B CN102322360B CN2011101352127A CN201110135212A CN102322360B CN 102322360 B CN102322360 B CN 102322360B CN 2011101352127 A CN2011101352127 A CN 2011101352127A CN 201110135212 A CN201110135212 A CN 201110135212A CN 102322360 B CN102322360 B CN 102322360B
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- 238000002347 injection Methods 0.000 title claims abstract description 23
- 239000007924 injection Substances 0.000 title claims abstract description 23
- 238000000034 method Methods 0.000 title claims abstract description 14
- 230000006835 compression Effects 0.000 claims abstract description 9
- 238000007906 compression Methods 0.000 claims abstract description 9
- 239000000446 fuel Substances 0.000 claims abstract description 9
- 239000007921 spray Substances 0.000 claims description 28
- 239000003921 oil Substances 0.000 claims description 18
- 239000000295 fuel oil Substances 0.000 claims description 7
- 230000005540 biological transmission Effects 0.000 claims description 3
- 238000002485 combustion reaction Methods 0.000 abstract description 11
- 239000007789 gas Substances 0.000 abstract description 11
- 239000002912 waste gas Substances 0.000 abstract description 5
- 230000001276 controlling effect Effects 0.000 description 6
- 239000000203 mixture Substances 0.000 description 3
- 230000000694 effects Effects 0.000 description 2
- 238000010304 firing Methods 0.000 description 2
- 238000005086 pumping Methods 0.000 description 2
- 230000001105 regulatory effect Effects 0.000 description 2
- 238000005507 spraying Methods 0.000 description 2
- OKTJSMMVPCPJKN-UHFFFAOYSA-N Carbon Chemical compound [C] OKTJSMMVPCPJKN-UHFFFAOYSA-N 0.000 description 1
- 239000004215 Carbon black (E152) Substances 0.000 description 1
- 238000010521 absorption reaction Methods 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 229910052799 carbon Inorganic materials 0.000 description 1
- 150000001875 compounds Chemical class 0.000 description 1
- 238000010790 dilution Methods 0.000 description 1
- 239000012895 dilution Substances 0.000 description 1
- 238000007599 discharging Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000001704 evaporation Methods 0.000 description 1
- 230000008020 evaporation Effects 0.000 description 1
- 239000008241 heterogeneous mixture Substances 0.000 description 1
- 229930195733 hydrocarbon Natural products 0.000 description 1
- 150000002430 hydrocarbons Chemical class 0.000 description 1
- 230000006698 induction Effects 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 230000001737 promoting effect Effects 0.000 description 1
- 230000002000 scavenging effect Effects 0.000 description 1
- 239000000779 smoke Substances 0.000 description 1
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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
- Y02T10/40—Engine management systems
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- Output Control And Ontrol Of Special Type Engine (AREA)
- Valve Device For Special Equipments (AREA)
- Electrical Control Of Air Or Fuel Supplied To Internal-Combustion Engine (AREA)
Abstract
The invention provides an in-cylinder direction injection gasoline engine and a control method thereof so as to reduce the throttling loss, increase the combustion stability and reduce the oil consumption. As the in-cylinder direction injection gasoline engine of the invention is provided with two-stage type variable valve lift and variable valve timing, under a low load working condition, an electronic control unit controls an exhaust valve to be closed before a top dead center of an exhaust stroke and an intake valve to be closed in the first half of a suction stroke, therefore, a section of negative valve overlapping interval is formed nearby the top dead center of a compression stroke, a part of exhaust gas is remained in an air cylinder; the electronic control unit respectively controls a fuel injector to carry out the first injection in the minus 30-30 degree CA range of the top dead center of the air suction and the second injection in the compression stroke, therefore, the high remained waste gas in the cylinder can be used, the thermal efficiency is increased, and meanwhile the combustion stability is ensured; and under a high load working condition, the electronic control unit controls the intake valve and the exhaust valve to work under the big lift to carry out the normal fuel injection and phase control.
Description
Technical field
The invention belongs to motor car engine manufacturing technology field, specially refer to a kind of direct spray petrol engine in cylinder and controlling method thereof.
Background technique
Compare with traditional electronic control intake port injection mode, direct spray petrol engine in cylinder has more flexibility in the formation of mixed gas.Direct spray petrol engine in cylinder can be realized the burning of lean-burn mixed gas under partial load condition, and can use bigger throttle opening, thereby reduction pumping loss, under high load working condition, aspirating stroke is sprayed, and utilizes gasoline evaporation heat absorption to reduce the temperature of mixed gas in the cylinder, thereby can reduce the tendency to detonate of petrol engine in the cylinder, therefore directly jetting gasoline engine can adopt higher compression ratio, and these advantages all are conducive to improve the fuel economy of petrol engine.
But be limited by fuel qualities and lean-burn emission control technique and also do not obtain the excellent engineering application, the direct spray petrol engine in cylinder of main flow is still taked conventional equivalent proportion mixture combustion pattern under sub load at present, this combustion mode is the same with intake port injection, need utilize closure that air inflow is controlled, so that the size of control motor output load, because the restriction loss of closure, its pumping loss merit is identical with the basic size of intake port injection, and this improves effect with regard to the thermal efficiency that greatly reduces petrol engine.
That the generation type of direct spray petrol engine in cylinder mixed gas mainly contains is wall-guided, air-flow guiding and spray-guided formula are several.Because the in-cylinder direct injection discharge time is short, especially under sub load, in-cylinder pressure is lower, intake temperature is low, fuel-oil atmozation is bad, and a part of elaioleucite is ejected on piston and the combustion chamber wall surface, causes being detained unevaporated drop fuel oil or denseer mixed gas at wall, and then causes hydrocarbon and increase carbon smoke exhaust.The burning of heterogeneous mixture in the cylinder simultaneously can cause the NOx discharging to increase again.
Therefore how to improve the combustion case under the little load of in-cylinder direct fuel-injection engine part, reduce restriction loss, improve fuel economy, and reduce the NOx of layering generation and the HC compound that wet wall produces, direct spray petrol engine in cylinder is most important for promoting.
Summary of the invention
The objective of the invention is to propose a kind of direct spray petrol engine in cylinder and controlling method thereof, to reduce restriction loss, improve combustion stability and reduce oil consumption.
Direct spray petrol engine in cylinder of the present invention comprises ECU (Electrical Control Unit), oil sprayer in valve mechanism and the cylinder, described ECU (Electrical Control Unit) respectively with oil sprayer, engine control system links to each other, key is that corresponding each cylinder body of described valve mechanism is provided with by first intake valve, the intake valve that second intake valve is formed, by first exhaust valve, the exhaust valve that second exhaust valve is formed, described intake valve utilizes admission cam shaft control, described exhaust valve utilizes exhaust cam shaft control, described first intake valve, second intake valve utilizes the cam control that is arranged at two different lift scopes on the admission cam shaft respectively, described first exhaust valve, second exhaust valve utilizes the cam control that is arranged at two different lift scopes on the exhaust cam shaft respectively, and described ECU (Electrical Control Unit) is by the cam work on transmission mechanism control admission cam shaft and the exhaust cam shaft.
Further, in two cams on the described admission cam shaft, first intake cam has first lift and second lift, and second intake cam has first lift and zero lift; In two cams on the described exhaust cam shaft, first exhaust cam has first lift and second lift, and second exhaust cam has first lift and zero lift; Described second lift is greater than zero and less than first lift.
Further, described first intake cam is controlled first intake valve, and second intake cam is controlled second intake valve, and first exhaust cam is controlled first exhaust valve, and second exhaust cam is controlled second exhaust valve; Described ECU (Electrical Control Unit) is divided into first group with first intake valve, first exhaust valve, second intake valve, second exhaust valve is divided into second group controls simultaneously.
In the controlling method of above-mentioned direct spray petrol engine in cylinder, the engine load signal that described ECU (Electrical Control Unit) transmits according to engine control system is controlled the cam work on each admission cam shaft and the exhaust cam shaft, under the little load condition of motor, ECU (Electrical Control Unit) is controlled first intake valve and is adopted second lift, control second intake valve and adopt zero lift, control first exhaust valve and adopt second lift, control second exhaust valve and adopt zero lift; Under the motor high load working condition, ECU (Electrical Control Unit) is controlled first intake valve, second intake valve, first exhaust valve, second exhaust valve and is all adopted first lift.ECU (Electrical Control Unit) is by the lift of control intake valve and exhaust valve, make under the little load condition of motor, each cylinder has only an intake valve and an exhaust valve job, and all be in little lift, under the prerequisite that air inflow when satisfying little load condition requires, reduced the friction merit of valve mechanism, and remaining EGR leads in the effective control cylinder of energy size and cylinder temperature, thereby can improve induction air flow ratio, promote fuel-oil atmozation; Under the motor high load working condition, control four valves and under high-lift, work, and in conjunction with Variable Valve Time, can effectively suppress the tendency to detonate under the low speed, and guarantee maximum power.
Further, under the little load condition of motor, ECU (Electrical Control Unit) control exhaust valve cuts out in the exhaust stroke budc, the control intake valve is closed at the aspirating stroke front half part, and carry out the first time at air inlet top dead center-30～30 a ° CA scope inner control oil sprayer respectively and spray, carry out the second time at compression stroke control oil sprayer and spray; Under the motor high load working condition, ECU (Electrical Control Unit) control intake valve and exhaust valve are all opened at exhaust stroke top dead center place, and the control oil sprayer carries out the fuel oil injection in aspirating stroke.Under the little load condition of motor, oil sprayer is taked spray-guided twice injection, be injected near the compression top center for the first time, form homogeneous charge under the high temperature, spray for the second time and can around spark plug, form denseer mixed gas, thereby can carry out the layering homogeneous combustion, and can guarantee combustion stability under very high EGR leads; By regulating valve opening and shut-in time, can near the compression stroke top dead center, form one section negative valve overlap interval, close at the interval exhaust valve of this section, and intake valve does not also have unlatching, understands some waste gas and remains in the cylinder.Oil sprayer sprays in air inlet top dead center-30～30 ° CA scope, because the exhaust gas temperature height, pressure is big, can form the even mixed gas of comparison like this, and can avoid wet wall phenomenon; This part remaining waste gas can also play the gas volume dilution and reduce the density of the induced air effect in the cylinder simultaneously, can increase throttle opening, thereby can reduce restriction loss.Specifically, under the little load condition of motor, emitted dose accounts for 10～30% of total fuel injection quantity for the second time, can improve the tolerance that combustion system leads EGR greatly, thereby further reduce restriction loss.
When the big load of motor, take two intake valve work, and all be high-lift, can reduce the inlet and outlet resistance like this.Form certain valve overlap by regulating valve opening and shut-in time, can utilize the suction tude boost pressure to carry out the fresh air scavenging greater than exhaust back pressure like this, can reduce the residual gas amount, reduce mixture temperature in the cylinder, and carry out fuel oil in aspirating stroke and spray, further reduce mixture temperature in the cylinder, suppress the generation of pinking.
Direct spray petrol engine in cylinder of the present invention is provided with lift range variable and the Variable Valve Time of two-part, with the control valve lift and close, the opening time, its controlling method can be utilized the waste gas of high residue in the cylinder, improves combustion stability and reduces oil consumption.
Description of drawings
Fig. 1 is in-cylinder direct injection valve lift and the injection time schematic representation of the present invention under the little load condition of motor.
Fig. 2 is in-cylinder direct injection valve lift and the injection time schematic representation of the present invention under the motor high load working condition.
Indicate among the figure: 1, the firing pressure under the little load condition; 2, exhaust second lift under the little load condition; 3, air inlet second lift under the little load condition; 4, spray the first time under the little load condition; 5, spray the second time under the little load condition; 6, the firing pressure under the high load working condition; 7, first lift of the exhaust under the high load working condition; 8, first lift of the air inlet under the high load working condition; 9, the injection under the high load working condition.
Embodiment
Describe the present invention in detail below in conjunction with specific embodiments and the drawings.
Embodiment 1:
In the present embodiment, direct spray petrol engine in cylinder comprises ECU (Electrical Control Unit), oil sprayer in valve mechanism and the cylinder, described ECU (Electrical Control Unit) respectively with oil sprayer, engine control system links to each other, key is that corresponding each cylinder body of described valve mechanism is provided with by first intake valve, the intake valve that second intake valve is formed, by first exhaust valve, the exhaust valve that second exhaust valve is formed, described intake valve utilizes admission cam shaft control, described exhaust valve utilizes exhaust cam shaft control, described first intake valve, second intake valve utilizes the cam control that is arranged at two different lift scopes on the admission cam shaft respectively, described first exhaust valve, second exhaust valve utilizes the cam control that is arranged at two different lift scopes on the exhaust cam shaft respectively, and described ECU (Electrical Control Unit) is by the cam work on transmission mechanism control admission cam shaft and the exhaust cam shaft.
In two cams on the described admission cam shaft, first intake cam has first lift and second lift, and second intake cam has first lift and zero lift; In two cams on the described exhaust cam shaft, first exhaust cam has first lift and second lift, and second exhaust cam has first lift and zero lift; Described second lift is greater than zero and less than first lift.First intake cam is controlled first intake valve, and second intake cam is controlled second intake valve, and first exhaust cam is controlled first exhaust valve, and second exhaust cam is controlled second exhaust valve; Described ECU (Electrical Control Unit) is divided into first group with first intake valve, first exhaust valve, second intake valve, second exhaust valve is divided into second group controls simultaneously.
As shown in Figure 2, in the controlling method of above-mentioned direct spray petrol engine in cylinder, the engine load signal that described ECU (Electrical Control Unit) transmits according to engine control system is controlled the cam work on each admission cam shaft and the exhaust cam shaft, under the little load condition of motor, ECU (Electrical Control Unit) is controlled first intake valve and is adopted air inlet second lift 3, control second intake valve and adopt zero lift, control first exhaust valve and adopt exhaust second lift 2, control second exhaust valve and adopt zero lift; Under the motor high load working condition, ECU (Electrical Control Unit) is controlled first intake valve, second intake valve all adopts air inlet first lift 8, first exhaust valve, second exhaust valve all to adopt exhaust first lift 7.
Under the little load condition of motor, ECU (Electrical Control Unit) control exhaust valve is near preceding the cutting out of exhaust stroke top dead center (be the 300 ° of CA of crank angle among Fig. 1), the control intake valve is closed near aspirating stroke front half part (be the 400 ° of CA of crank angle among Fig. 1), near the compression stroke top dead center, form one section negative valve overlap interval like this, close at the interval exhaust valve of this section, and intake valve does not also have unlatching, understands some waste gas and remains in the cylinder.ECU (Electrical Control Unit) respectively in air inlet top dead center-30～30 ° CA scope (being near the 360 ° of CA of crank angle among Fig. 1) control oil sprayer carry out spraying 4 the first time, carry out spraying 5 second time near compression stroke (be the 660 ° of CA of crank angle among Fig. 1) control oil sprayer, the second time, emitted dose accounted for 10～30% of total fuel injection quantity; Under the motor high load working condition, ECU (Electrical Control Unit) control intake valve and exhaust valve are all opened exhaust stroke top dead center place (be the 360 ° of CA of crank angle among Fig. 2 near), form certain valve overlap, and the control oil sprayer carries out the fuel oil injection in aspirating stroke.
Claims (4)
1. the controlling method of a direct spray petrol engine in cylinder, this direct spray petrol engine in cylinder comprises ECU (Electrical Control Unit), oil sprayer in valve mechanism and the cylinder, described ECU (Electrical Control Unit) respectively with oil sprayer, engine control system links to each other, corresponding each cylinder body of described valve mechanism is provided with by first intake valve, the intake valve that second intake valve is formed, by first exhaust valve, the exhaust valve that second exhaust valve is formed, described intake valve utilizes admission cam shaft control, described exhaust valve utilizes exhaust cam shaft control, described first intake valve, second intake valve utilizes the cam control that is arranged at two different lift scopes on the admission cam shaft respectively, described first exhaust valve, second exhaust valve utilizes the cam control that is arranged at two different lift scopes on the exhaust cam shaft respectively, and described ECU (Electrical Control Unit) is by the cam work on transmission mechanism control admission cam shaft and the exhaust cam shaft; In two cams on the described admission cam shaft, first intake cam has first lift and second lift, and second intake cam has first lift and zero lift; In two cams on the described exhaust cam shaft, first exhaust cam has first lift and second lift, and second exhaust cam has first lift and zero lift; Described second lift is greater than zero and less than first lift; It is characterized in that engine load signal that described ECU (Electrical Control Unit) transmits according to engine control system controls the cam work on each admission cam shaft and the exhaust cam shaft, under the little load condition of motor, ECU (Electrical Control Unit) is controlled first intake valve and is adopted second lift, control second intake valve and adopt zero lift, control first exhaust valve and adopt second lift, control second exhaust valve and adopt zero lift; Under the motor high load working condition, ECU (Electrical Control Unit) is controlled first intake valve, second intake valve, first exhaust valve, second exhaust valve and is all adopted first lift.
2. the controlling method of direct spray petrol engine in cylinder according to claim 1, it is characterized in that described first intake cam controls first intake valve, second intake cam is controlled second intake valve, and first exhaust cam is controlled first exhaust valve, and second exhaust cam is controlled second exhaust valve; Described ECU (Electrical Control Unit) is divided into first group with first intake valve, first exhaust valve, second intake valve, second exhaust valve is divided into second group controls simultaneously.
3. the controlling method of direct spray petrol engine in cylinder according to claim 1 and 2, it is characterized in that under the little load condition of motor, ECU (Electrical Control Unit) control exhaust valve cuts out in the exhaust stroke budc, the control intake valve is closed at the aspirating stroke front half part, and carry out the first time at air inlet top dead center-30～30 a ° CA scope inner control oil sprayer respectively and spray, carry out the second time at compression stroke control oil sprayer and spray; Under the motor high load working condition, the controlling fuel injection by electric control unit device carries out fuel oil in aspirating stroke and sprays.
4. the controlling method of direct spray petrol engine in cylinder according to claim 3 is characterized in that under the little load condition of motor, and emitted dose accounts for 10～30% of total fuel injection quantity for the second time.
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| Application Number | Priority Date | Filing Date | Title |
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| CN2011101352127A CN102322360B (en) | 2011-05-24 | 2011-05-24 | In-cylinder direction injection gasoline engine and control method thereof |
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| CN2011101352127A CN102322360B (en) | 2011-05-24 | 2011-05-24 | In-cylinder direction injection gasoline engine and control method thereof |
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| CN102322360B true CN102322360B (en) | 2013-09-11 |
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| CN103334846B (en) * | 2013-07-23 | 2016-03-30 | 清华大学 | A kind of judgement of super detonation and controlling method |
| CN112682183B (en) * | 2019-10-17 | 2023-04-07 | 长城汽车股份有限公司 | Control method for wrap angle and valve overlap angle of engine intake valve |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101451453A (en) * | 2007-12-05 | 2009-06-10 | 现代自动车株式会社 | Valve system |
| CN101779023A (en) * | 2007-08-13 | 2010-07-14 | 丰田自动车株式会社 | Control device for internal combustion engine equipped with turbocharger |
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| JPH07107367B2 (en) * | 1989-04-07 | 1995-11-15 | 本田技研工業株式会社 | Internal combustion engine intake system |
| JPH11287139A (en) * | 1998-04-01 | 1999-10-19 | Honda Motor Co Ltd | Variable valve lift device for engine |
| JP4164894B2 (en) * | 1998-04-03 | 2008-10-15 | 日産自動車株式会社 | Spark ignition internal combustion engine |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101779023A (en) * | 2007-08-13 | 2010-07-14 | 丰田自动车株式会社 | Control device for internal combustion engine equipped with turbocharger |
| CN101451453A (en) * | 2007-12-05 | 2009-06-10 | 现代自动车株式会社 | Valve system |
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