CN102182608A - Combustion system of gasoline direct injection engine and control method thereof - Google Patents
Combustion system of gasoline direct injection engine and control method thereof Download PDFInfo
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- CN102182608A CN102182608A CN2011100628657A CN201110062865A CN102182608A CN 102182608 A CN102182608 A CN 102182608A CN 2011100628657 A CN2011100628657 A CN 2011100628657A CN 201110062865 A CN201110062865 A CN 201110062865A CN 102182608 A CN102182608 A CN 102182608A
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- 238000002485 combustion reaction Methods 0.000 title claims abstract description 36
- 238000000034 method Methods 0.000 title claims abstract description 16
- 238000002347 injection Methods 0.000 title claims abstract description 13
- 239000007924 injection Substances 0.000 title claims abstract description 13
- 239000007921 spray Substances 0.000 claims description 40
- 239000003921 oil Substances 0.000 claims description 32
- 239000000203 mixture Substances 0.000 claims description 14
- 238000010304 firing Methods 0.000 claims description 12
- 239000000446 fuel Substances 0.000 claims description 10
- 239000000295 fuel oil Substances 0.000 claims description 10
- 230000006835 compression Effects 0.000 claims description 8
- 238000007906 compression Methods 0.000 claims description 8
- 238000005507 spraying Methods 0.000 claims description 6
- 238000007599 discharging Methods 0.000 description 8
- 239000003595 mist Substances 0.000 description 7
- 238000011160 research Methods 0.000 description 4
- 238000005516 engineering process Methods 0.000 description 3
- 239000007789 gas Substances 0.000 description 3
- OKTJSMMVPCPJKN-UHFFFAOYSA-N Carbon Chemical compound [C] OKTJSMMVPCPJKN-UHFFFAOYSA-N 0.000 description 2
- UFHFLCQGNIYNRP-UHFFFAOYSA-N Hydrogen Chemical compound [H][H] UFHFLCQGNIYNRP-UHFFFAOYSA-N 0.000 description 2
- 229910052799 carbon Inorganic materials 0.000 description 2
- 230000003197 catalytic effect Effects 0.000 description 2
- 238000010790 dilution Methods 0.000 description 2
- 239000012895 dilution Substances 0.000 description 2
- 229910052739 hydrogen Inorganic materials 0.000 description 2
- 239000001257 hydrogen Substances 0.000 description 2
- 230000008569 process Effects 0.000 description 2
- 238000012795 verification Methods 0.000 description 2
- 206010036590 Premature baby Diseases 0.000 description 1
- 239000003054 catalyst Substances 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 230000007613 environmental effect Effects 0.000 description 1
- 238000001704 evaporation Methods 0.000 description 1
- 230000008020 evaporation Effects 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 230000035800 maturation Effects 0.000 description 1
- 230000001473 noxious effect Effects 0.000 description 1
- 238000009527 percussion Methods 0.000 description 1
- 238000005086 pumping Methods 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
- 230000004044 response Effects 0.000 description 1
- 239000004071 soot Substances 0.000 description 1
- 230000001052 transient effect Effects 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
- Y02T10/12—Improving ICE efficiencies
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- Combustion Methods Of Internal-Combustion Engines (AREA)
Abstract
The invention provides a combustion system of a gasoline direct injection engine and a control method thereof, for improving the combustion and discharge status of a cold starting stage. The combustion system of the gasoline direct injection engine comprises a cylinder cover, a piston, a cylinder sleeve, a spark plug and an oil injector; the cylinder cover is provided with an intake valve, an exhaust valve, an intake passage connected with the intake valve, and an exhaust passage connected with the exhaust valve; the top surface of the piston is provided with an intake valve evading pit corresponding to the position of the intake valve and an exhaust valve evading pit corresponding to the position of the exhaust valve; the spark plug is mounted on one side of the cylinder cover between the intake valve and the exhaust valve and is close to the exhaust valve, the top surface of the piston rod between the downside of the spark plug and the oil sprayer is hollowed to form a concave pit, and the oil injector is arranged under the intake valve and faces towards the concave pit. The control method of the combustion system comprises the steps: A, a twice-injection layered combustion manner is adopted under a cold starting condition; and B, and a single-injection homogeneous equivalence-ratio combustion manner in which gasoline is injected one time in a gas inlet stroke is adopted under the other conditions.
Description
Technical field
The invention belongs to motor car engine manufacturing technology field, specially refer to direct spray petrol engine in cylinder combustion system and controlling method thereof.
Background technique
Along with the environmental problem swift and violent increase of sternness and automobile pollution day by day, strict more at the relevant laws and regulations of automotive energy-saving emission-reducing.Compare with traditional gas-duct jetting petrol engine (PFI), oil spout directly jetting gasoline engine (GDI) has better Economy and emission performance, and having become at present is petrolic main developing direction and research focus.
In the last few years, by to being the research of the novel lean combustion pattern of representative, improved the fuel economy of petrol engine widely with layering lean combustion direct spray petrol engine in cylinder and homogeneous compression ignition petrol engine.The utilization of the super lean air fuel ratio of GDI motor and the change of working method have brought lot of advantages, have reduced pumping loss as the cancellation throttling, and the cylinder temperature that fuel evaporation causes reduces, and has improved the compression ratio that petrol engine can be worked; Fuel oil cools off air inlet in intake stroke, has improved charging efficiency etc.These advantages make the fuel economy of score layer lean-burn GDI motor can improve 10～25%, and power output also increases about 10% than the petrol engine of intake port injection.In addition, the transient response ability of GDI motor raising, air fuel ratio control is accurate, cold start-up is quick etc. has all shown its superiority than intake port injection petrol engine.But this is that the GDI of target has also run into some problems in actual applications with the lean-burn: required lean-burn catalyzer prematurity still, thereby cause the NOx discharging high, and layering lean-burn mixture control difficulty is very big, and medium and small load unburned carbon hydrogen is higher.
There are the problems referred to above in GDI in view of the layering lean-burn, and after 2000, Europe has taked homogeneous charge and stoichiometric proportion (homogeneous equivalent proportion) to be the technology path of feature.This GDI motor is compared with traditional PFI motor can improve fuel economy and power character about 10% respectively.The discharging aspect, owing to adopt the homogeneous equivalent proportion still can adopt traditional three-way catalyst, the feasibility of industrialization is higher, the GDI technology is because of fuel injection amount and oil gas mixed process in can more accurate control cylinder, have bigger reduction cold start-up HC discharging potentiality, but there are some researches show that also the discharging of unburned carbon hydrogen accounts for 60%～80% of total discharging in direct spray petrol engine in cylinder cold start-up of homogeneous equivalent proportion and the warming-up process, can directly affect motor and satisfy stricter Abgasgesetz, therefore the discharging of cold start-up stage becomes the emphasis and the difficult point of current Vehicle Emission Control technical research.
Summary of the invention
The objective of the invention is to propose a kind of direct spray petrol engine in cylinder combustion system and controlling method thereof,, discharge thereby improve to improve the combustion position in cold start-up stage.
Direct spray petrol engine in cylinder combustion system of the present invention comprises cylinder cap, piston, cylinder liner, spark plug and oil sprayer, and intake valve, exhaust valve and the intake duct that is connected with intake valve, the air outlet flue that is connected with exhaust valve are housed on the cylinder cap; The position of the corresponding intake valve of the end face of piston is provided with the intake valve valve pit, and the position of corresponding exhaust valve is provided with the exhaust valve valve pit; Key be that described spark plug is installed between intake valve and the exhaust valve and the cylinder cap near a side of exhaust valve on, described spark plug below has been recessed to form pit to the piston-top surface between the oil sprayer, and described oil sprayer is arranged on place, intake valve below and towards pit.
The temperature of cylinder exhaust side is higher, and spark plug can at first be lighted the mixed gas of exhaust side nearby near exhaust valve one side, reduces the possibility of pinking.
For guiding mist of oil better, described pit is provided with the spray-guided edge that raises up towards spark plug near the edge of exhaust side, and described spray-guided edge is 0 °～45 ° with the cylinder-bore axis angle.
For further improving burning quality, described intake duct is that height rolls flow inlet port, and described oil sprayer is the multiple orifice nozzle in 5～8 holes.
The controlling method of above-mentioned direct spray petrol engine in cylinder combustion system comprises the steps:
A: adopt the mode of spraying stratified mixture combustion twice under the cold start-up operating mode: begin to spray for the first time at 50 °～90 ° crank angles of air inlet atdc, before compression stroke is sprayed for the second time, in cylinder, form the homogeneous weak mixture; Begin to spray for the second time at igniting budc 30 °～50 ° crank angles, in the firing chamber, form near the spark plug denseer and to around thinning gradually stratified mixtures; Plug ignition makes the fuel ignition burning;
B: adopt under other operating mode at the once oily single injection event homogeneous equivalent proportion combustion manner of aspirating stroke spray.
In the described steps A, spray the fuel oil quality ratio that sprays with the second time for the first time and be 6:4.
Be to accelerate the ignition speed of ternary catalyzing unit under the cold start-up operating mode, in the described steps A, postpone firing angle 10 °～20 ° crank angles to the compression top center.
The pit of piston-top surface can be when oil burner sprays be guided fuel oil into the spark plug place, and has increased the area of contact of fuel oil and air, therefore can form homogeneous charge after the fuel injection in cylinder.After spraying for the first time, mist of oil is full of the firing chamber gradually, forms the homogeneous weak mixture; After spraying for the second time, when the mist of oil that increases newly accumulates in the spark plug place and does not have enough time to spread, in the firing chamber, form near the spark plug denseer and to around thinning gradually stratified mixtures, this moment plug ignition, can guarantee to realize the stable ignition and the perfect combustion of fuel oil, reduce discharging.The quality of adjusting twice oil spout is injection time when, and promptly the fuel oil mist of oil distribution situation in the firing chamber during may command plug ignition is promptly controlled combustion case.Discharge time is too early for the first time, and this moment, position of piston was higher, can cause the oil droplet of oil sprayer ejection directly to strike piston face, forms soot, and then influence burning and discharging; Discharge time is late excessively for the first time, this moment, position of piston was low excessively, and intake valve is about to close, air inlet is rolled stream the guiding function of spraying is weakened, can cause mist of oil collision and be adsorbed on the cylinder wall, and be scraped in the oil sump, cause oil dilution by piston, also reduce simultaneously the utilization ratio of fuel oil, increased oil consumption.Discharge time is too early for the second time, and mist of oil mixes before can causing lighting a fire, and can't form stratified mixtures, the stability of influence igniting; Discharge time is late excessively for the second time, the serious percussion piston of oil droplet surface forms a large amount of soots, also the mist of oil that increases newly can't be accumulated in the spark plug place, in the firing chamber, form near the spark plug denseer and to around thinning gradually stratified mixtures, the stability of influence igniting.Through verification experimental verification, begin to spray for the first time at 50 °～90 ° crank angles of air inlet atdc, begin to spray for the second time at 30 °～50 ° crank angles of igniting budc, when the fuel oil quality ratio that sprays the first time and spray for the second time is 6:4, it is the most stable to light a fire, it is the most complete to burn, and emission status is best.
Direct spray petrol engine in cylinder combustion system of the present invention is changed former machine and is easy to for a short time realize, only need to revise directly jetting gasoline engine piston-top surface shape, cooperate the oil spout strategy that is easy to realize, can obtain the mixed gas of reasonable layering, improve Ignition Stability and improve combustion position, satisfy Europe five even Europe six Abgasgesetzs.
Description of drawings
Fig. 1 is the structure sectional view of the combustion system of direct spray petrol engine in cylinder of the present invention.
Fig. 2 is the piston crown plan view of the combustion system of direct spray petrol engine in cylinder of the present invention.
Be labeled as among the figure: 1-cylinder cap, 2-piston, 3-firing chamber, 4-oil sprayer, 5-intake duct, 6-intake valve, 7-spark plug, 8-exhaust valve, 9-air outlet flue, 10-pit, 11-intake valve valve pit, 12-spray-guided edge, 13-exhaust valve valve pit.
Embodiment
Describe the present invention in detail below in conjunction with specific embodiments and the drawings.
Embodiment 1:
As shown in Figure 1, 2, the combustion system of the direct spray petrol engine in cylinder of present embodiment comprises cylinder cap 1, piston 2, spark plug 7 and oil sprayer 4, intake valve 6, exhaust valve 8 is housed and air outlet flue 9 that the height that is connected with intake valve 6 rolls flow inlet port 5, is connected with exhaust valve 8 on the cylinder cap 1; The position of the corresponding intake valve 6 of the end face of piston 2 is provided with intake valve valve pit 11, and the position of corresponding exhaust valve 8 is provided with exhaust valve valve pit 13.Cylinder cap 1 is a fluffy top shape, is positioned at the upper end of piston 2, and the space between itself and the piston 2 forms firing chamber 3.Spark plug 7 vertically is installed on the cylinder head 1 between intake valve 6 and the exhaust valve 8, and deflection exhaust valve 8 one sides; Spark plug 7 belows have been recessed to form pit 10 to the piston-top surface between the oil sprayer 4, and pit 10 is provided with spray-guided along 12 towards spark plug 7 of raising up near the edge of exhaust side, spray-guided along 12 with the cylinder-bore axis angle be 45 °; Oil sprayer 4 is the multiple orifice nozzle in 7 holes, tilts to be installed on the below of high billowing intake duct 5 and towards pit 10.
The controlling method of the combustion system of above-mentioned direct spray petrol engine in cylinder comprises the steps:
A: adopt the mode of spraying stratified mixture combustion twice under the cold start-up operating mode: begin to spray for the first time at 70 ° of crank angles of air inlet atdc, the guiding that utilizes piston crater and air inlet to roll stream effectively prevents Spray Impingement, reduce oil film and oil dilution, before compression stroke is sprayed for the second time, in cylinder, form the weak mixture of homogeneous; Begin to spray for the second time at 40 ° of crank angles of igniting budc, guiding by piston crater and spray-guided edge, in the firing chamber, form near the spark plug denseer and to around thinning gradually stratified mixtures, cooperate and postpone igniting (being that firing angle is 15 ° of crank angles behind the compression top center), to accelerate catalytic converter ignition speed, noxious emission during the minimizing cold start-up;
B: adopt under other operating mode at the once oily single injection event homogeneous equivalent proportion combustion manner of aspirating stroke spray, can continue operation technique maturation, lower-cost traditional three-way catalytic converter, to realize the maximization of power output.
In the described steps A, spray the fuel oil quality ratio that sprays with the second time for the first time and be 6:4.
Claims (7)
1. a direct spray petrol engine in cylinder combustion system comprises cylinder cap, piston, cylinder liner, spark plug and oil sprayer, and intake valve, exhaust valve and the intake duct that is connected with intake valve, the air outlet flue that is connected with exhaust valve are housed on the cylinder cap; The position of the corresponding intake valve of the end face of piston is provided with the intake valve valve pit, and the position of corresponding exhaust valve is provided with the exhaust valve valve pit; It is characterized in that described spark plug is installed between intake valve and the exhaust valve and the cylinder cap near a side of exhaust valve on, described spark plug below has been recessed to form pit to the piston-top surface between the oil sprayer, and described oil sprayer is arranged on place, intake valve below and towards pit.
2. direct spray petrol engine in cylinder combustion system according to claim 1 is characterized in that described pit is provided with the spray-guided edge that raises up towards spark plug near the edge of exhaust side, and described spray-guided edge is 0 °～45 ° with the cylinder-bore axis angle.
3. direct spray petrol engine in cylinder combustion system according to claim 1 and 2 is characterized in that described intake duct is that height rolls flow inlet port.
4. direct spray petrol engine in cylinder combustion system according to claim 1 and 2 is characterized in that described oil sprayer is the multiple orifice nozzle in 5～8 holes.
5. the controlling method of direct spray petrol engine in cylinder combustion system according to claim 1 is characterized in that comprising the steps:
A: adopt the mode of spraying stratified mixture combustion twice under the cold start-up operating mode: begin to spray for the first time at 50 °～90 ° crank angles of air inlet atdc, before compression stroke is sprayed for the second time, in cylinder, form the homogeneous weak mixture; Begin to spray for the second time at igniting budc 30 °～50 ° crank angles, in the firing chamber, form near the spark plug denseer and to around thinning gradually stratified mixtures; Plug ignition makes the fuel ignition burning;
B: adopt under other operating mode at the once oily single injection event homogeneous equivalent proportion combustion manner of aspirating stroke spray.
6. the controlling method of direct spray petrol engine in cylinder combustion system according to claim 5 is characterized in that in the described steps A, sprays for the first time with the fuel oil quality ratio that sprays for the second time to be 6:4.
7. according to the controlling method of claim 5 or 6 described direct spray petrol engine in cylinder combustion systems, it is characterized in that in the described steps A, postpone firing angle 10 °～20 ° crank angles to the compression top center.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2011100628657A CN102182608A (en) | 2011-03-16 | 2011-03-16 | Combustion system of gasoline direct injection engine and control method thereof |
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| Application Number | Priority Date | Filing Date | Title |
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| CN2011100628657A CN102182608A (en) | 2011-03-16 | 2011-03-16 | Combustion system of gasoline direct injection engine and control method thereof |
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Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103696847A (en) * | 2012-09-28 | 2014-04-02 | 重庆长安汽车股份有限公司 | In-cylinder direct injection engine combustion chamber |
| CN104271916A (en) * | 2012-04-13 | 2015-01-07 | 卡特彼勒能源方案有限公司 | Piston of an internal combustion engine |
| CN106523227A (en) * | 2016-12-16 | 2017-03-22 | 上海理工大学 | Multi-point ignition combustion system with double spraying devices |
| CN106762101A (en) * | 2016-11-21 | 2017-05-31 | 清华大学 | A kind of directly jetting gasoline engine combustion system and control method |
| CN107387229A (en) * | 2017-07-31 | 2017-11-24 | 天津大学 | A kind of combustion system of engine for using Fuel Petroleum instead suitable for diesel engine |
| CN107491572A (en) * | 2016-08-17 | 2017-12-19 | 宝沃汽车（中国）有限公司 | Fluid emulation computational methods in a kind of cylinder |
| CN112081693A (en) * | 2020-09-15 | 2020-12-15 | 奇瑞汽车股份有限公司 | Miller cycle gasoline engine |
| CN112177785A (en) * | 2020-09-30 | 2021-01-05 | 东风汽车集团有限公司 | Method and system for reducing particulate matter emission in low-temperature warm-up stage of gasoline direct injection engine |
| CN117569943A (en) * | 2024-01-15 | 2024-02-20 | 潍柴动力股份有限公司 | Porous eccentric piston and design method thereof |
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2011
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| JP2004239076A (en) * | 2003-02-03 | 2004-08-26 | Nissan Motor Co Ltd | Direct injection spark ignition type internal combustion engine |
| CN1560440A (en) * | 2004-02-27 | 2005-01-05 | 清华大学 | Method of layering forming mixed gas for gasoline directly jetting type engine based multisection jetting |
| CN101144413A (en) * | 2007-09-28 | 2008-03-19 | 清华大学 | Directly spraying petrol engine combustion camber in cylinder |
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Cited By (13)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104271916A (en) * | 2012-04-13 | 2015-01-07 | 卡特彼勒能源方案有限公司 | Piston of an internal combustion engine |
| CN103696847A (en) * | 2012-09-28 | 2014-04-02 | 重庆长安汽车股份有限公司 | In-cylinder direct injection engine combustion chamber |
| CN107491572A (en) * | 2016-08-17 | 2017-12-19 | 宝沃汽车（中国）有限公司 | Fluid emulation computational methods in a kind of cylinder |
| CN106762101A (en) * | 2016-11-21 | 2017-05-31 | 清华大学 | A kind of directly jetting gasoline engine combustion system and control method |
| CN106523227A (en) * | 2016-12-16 | 2017-03-22 | 上海理工大学 | Multi-point ignition combustion system with double spraying devices |
| CN107387229B (en) * | 2017-07-31 | 2022-12-06 | 天津大学 | Engine combustion system suitable for gasoline fuel used instead of diesel engine |
| CN107387229A (en) * | 2017-07-31 | 2017-11-24 | 天津大学 | A kind of combustion system of engine for using Fuel Petroleum instead suitable for diesel engine |
| CN112081693A (en) * | 2020-09-15 | 2020-12-15 | 奇瑞汽车股份有限公司 | Miller cycle gasoline engine |
| CN112081693B (en) * | 2020-09-15 | 2021-12-28 | 奇瑞汽车股份有限公司 | Miller cycle gasoline engine |
| CN112177785B (en) * | 2020-09-30 | 2022-05-31 | 东风汽车集团有限公司 | Method and system for reducing particulate matter emission of gasoline direct injection engine in low-temperature warm-up stage |
| CN112177785A (en) * | 2020-09-30 | 2021-01-05 | 东风汽车集团有限公司 | Method and system for reducing particulate matter emission in low-temperature warm-up stage of gasoline direct injection engine |
| CN117569943A (en) * | 2024-01-15 | 2024-02-20 | 潍柴动力股份有限公司 | Porous eccentric piston and design method thereof |
| CN117569943B (en) * | 2024-01-15 | 2024-05-17 | 潍柴动力股份有限公司 | Porous eccentric piston and design method thereof |
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Application publication date: 20110914 |