CN1556313A - Direct spraying type diesel engine combustion system - Google Patents
Direct spraying type diesel engine combustion system Download PDFInfo
- Publication number
- CN1556313A CN1556313A CNA2004100023654A CN200410002365A CN1556313A CN 1556313 A CN1556313 A CN 1556313A CN A2004100023654 A CNA2004100023654 A CN A2004100023654A CN 200410002365 A CN200410002365 A CN 200410002365A CN 1556313 A CN1556313 A CN 1556313A
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- Prior art keywords
- diesel engine
- center
- firing chamber
- oil
- oil nozzle
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
- 238000002485 combustion reaction Methods 0.000 title claims abstract description 30
- 238000005507 spraying Methods 0.000 title description 5
- 239000007921 spray Substances 0.000 claims abstract description 22
- 238000010304 firing Methods 0.000 claims description 21
- 238000002347 injection Methods 0.000 claims description 8
- 239000007924 injection Substances 0.000 claims description 8
- 238000000034 method Methods 0.000 claims description 5
- 230000006835 compression Effects 0.000 claims description 4
- 238000007906 compression Methods 0.000 claims description 4
- 230000008569 process Effects 0.000 claims description 3
- 230000007704 transition Effects 0.000 claims 2
- MWUXSHHQAYIFBG-UHFFFAOYSA-N nitrogen oxide Inorganic materials O=[N] MWUXSHHQAYIFBG-UHFFFAOYSA-N 0.000 abstract description 12
- 239000007789 gas Substances 0.000 abstract description 10
- 241001270131 Agaricus moelleri Species 0.000 abstract description 3
- 239000002245 particle Substances 0.000 abstract 1
- 239000003921 oil Substances 0.000 description 15
- 239000000295 fuel oil Substances 0.000 description 11
- 239000000446 fuel Substances 0.000 description 6
- 239000013618 particulate matter Substances 0.000 description 6
- 239000000203 mixture Substances 0.000 description 5
- 230000015572 biosynthetic process Effects 0.000 description 2
- 239000003344 environmental pollutant Substances 0.000 description 2
- 230000008020 evaporation Effects 0.000 description 2
- 238000001704 evaporation Methods 0.000 description 2
- ZZUFCTLCJUWOSV-UHFFFAOYSA-N furosemide Chemical compound C1=C(Cl)C(S(=O)(=O)N)=CC(C(O)=O)=C1NCC1=CC=CO1 ZZUFCTLCJUWOSV-UHFFFAOYSA-N 0.000 description 2
- 230000035515 penetration Effects 0.000 description 2
- 231100000719 pollutant Toxicity 0.000 description 2
- 102000001999 Transcription Factor Pit-1 Human genes 0.000 description 1
- 108010040742 Transcription Factor Pit-1 Proteins 0.000 description 1
- 238000010521 absorption reaction Methods 0.000 description 1
- QVGXLLKOCUKJST-UHFFFAOYSA-N atomic oxygen Chemical compound [O] QVGXLLKOCUKJST-UHFFFAOYSA-N 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 238000005336 cracking Methods 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 239000002283 diesel fuel Substances 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000008570 general process Effects 0.000 description 1
- 239000001301 oxygen Substances 0.000 description 1
- 229910052760 oxygen Inorganic materials 0.000 description 1
- 239000000243 solution Substances 0.000 description 1
- 239000004071 soot Substances 0.000 description 1
Images
Classifications
-
- 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
Landscapes
- Combustion Methods Of Internal-Combustion Engines (AREA)
Abstract
Disclosed PCI combustion system is suitable to direct spray type engine. A dummy club 5 with flattop is setup at center on bottom of combustion chamber. Dummy clubs 7 formed from guiding circular arcs are setup around wall of combustion chamber. Ejective pocket of oil from one opening of porous oil nozzle located in front center strikes to flattop, and entrainment of air is entered from upper and lower sides. Ejective pocket of oil from other nozzle openings strikes to wall above guiding circular arcs and leaves wall from guiding circular arcs. The invention takes full advantage of large amount pre-mixed gas, few oil film is on wall. Thus, less discharge amount of particles and nitrogen oxides NOx is discharged, even in operating condition of high speed and high load.
Description
Technical field
The present invention design be the combustion system of a kind of PCI of being called of using on the direct injection diesel engine.
Background technique
Existing diesel engine with direct injection, its basic combustion principle are the diffusive combustions of diesel oil spraying.General process is in diesel engine compression stroke budc, and oil nozzle begins to spray into high pressure fuel in cylinder.The fuel oil of ejection and the air mixing in the cylinder form inflammable mixture and take fire.Because the temperature when this part fuel oil sprays in the cylinder in the cylinder is relatively low, so they generally have adequate time to mix with air, the generation premixed gas.But along with the beginning of in-cylinder combustion, the pressure and temperature in the cylinder raises rapidly.Therefore in cylinder, continue that part of fuel oil that sprays in burning beginning back, often with just take fire before air fully mixes.This part burning generates particulate matter PM easily owing to lack air.In addition, because the volumetric efficiency of diesel engine intake is generally more greater than 1, so there is the more rich mixed area of partial oxygen tolerance in the combustion process in the cylinder.This part zone generates nitrogen oxide NO easily under high temperature condition
xAbove-mentioned reason makes and has two kinds of a large amount of pollutants simultaneously in the exhaust of diesel engine.And, because the formation condition of two kinds of pollutants is far from each other,, cause the increase of another discharge amount easily therefore in order to reduce wherein a kind of measure of taking.In addition, for the miniature high-speed diesel engine, because the jet pressure of fuel oil is higher, the penetration distance of spraying is bigger, therefore forms oil film easily on combustion chamber wall surface.Under high rotating speed of motor and high load operating mode, the wall-film amount is more and available, and to participate in time of burning from wall heat absorption evaporation shorter, therefore has the part oil film and have little time with air mixing at high temperature to break up cracking and generate soot.This has increased the concentration of particulate matter in the diesel exhaust gas on the one hand, has also reduced combustion efficiency in addition, makes the oil consumption of diesel engine increase.
Summary of the invention
The purpose of this invention is to provide and a kind ofly can reduce particulate matter PM and nitrogen oxide NO in the diesel exhaust gas simultaneously
xThe new combustion systems of concentration, the energy structure is realized the low temperature pre-mixing combustion of diesel engine.
Technical solution of the present invention is that diesel engine with direct injection PCI of the present invention (Peripheral-CentricInjection) combustion system comprises cylinder 13, cylinder head 15, oil nozzle 11, piston 14 and firing chamber 1.Described oil nozzle is provided with a plurality of nozzle openings, and one of them 12 is positioned at oil nozzle front end central authorities, and just nozzle hole cone angle is 0, the central lines of the axis of this spray orifice and firing chamber taper.Other spray orifice 10 axis arranged on an imaginary conical surface, the center line of this conical surface center line and firing chamber taper and the dead in line of center of orifices, and the drift angle of this conical surface is 100 °～160 °.This system adopts the gas handling system of 4 valves, and requires oil nozzle just to put.In addition, the firing chamber bottom center that is adopted is a boss 5, and the last end face of this boss is plane (also can be convex surface or concave surface).Wall is provided with the annular boss 7 that is formed by one section guiding circular arc 8 around the firing chamber, and the diameter of guiding circular arc is 0.5～2.5mm.
The present invention reach beneficial effect be, existing diesel engine with direct injection is not high to the utilization ratio of air in the cylinder, point of ignition occurs early in the combustion process in addition, it is very fast that temperature and pressure in the cylinder is risen, and peak value is higher.Therefore, generate a large amount of particulate matter PM and nitrogen oxide NO
x, and because the burning of fuel is insufficient, the combustion efficiency and the economic performance of motor are relatively poor.And in the present invention, the fuel impingement of ejection will form a discoid spray 4, and entrainment air from upper and lower surface to the end face of bottom surface boss 7 from oil nozzle center of orifices 12, make full use of near the air in space, boss top.From the fuel oil of spray orifice 10 ejections all around, behind the bump sidewall, come off from wall at the guiding circular arc place, secondary-atomizing and air mixing form a large amount of thin combustible gases 3 in the space of bottom, firing chamber pit 2.Therefore can make full use of the air in the firing chamber, reduce the generation of particulate matter PM.In addition, because all sprayings will be lost the part momentum after clashing into wall, thus the formation of the inflammable mixture that will suitably slow down, thus the appearance of burning point of ignition postponed.To reduce the maximum temperature in the combustion process cylinder like this, thereby reduce NO
xAt last and since around fuel oil break away from from wall at the guiding circular arc place, so the oil film amount that forms on the wall is considerably less, the combustion efficiency of system is improved.Under identical fuel supply advance angle condition, the average fuel consumption rate of native system is lower than former machine about 16%.In addition, measure according to the 13-mode test cycle of standard, adopt the diesel engine of this combustion system, the discharge amount of its particulate matter PM will be lower than 0.15g/kwh, NO
xDischarge amount will be lower than 7g/kwh.That is to say and to reach Europe II emission standard.
Description of drawings
Fig. 1 is the partial schematic diagram of combustion system of directly jetting diesel engine of the present invention.
Fig. 2 is the structural representation of combustion system of directly jetting diesel engine of the present invention.
Embodiment
The present invention is described in detail below in conjunction with drawings and Examples.
In Fig. 1, diesel engine with direct injection of the present invention includes cylinder 13, piston 14, cylinder head 15, oil nozzle 11 and firing chamber 1.1 is the firing chamber among Fig. 2, and certain closing in is arranged.4 is the boss of firing chamber bottom center, and end face is the plane, also can be concave surface or convex surface.8 is the guiding circular arc on the wall around the firing chamber, and radius of arc is 0.5～2.5mm.The 7th, for the boss that guarantees that guiding circular arc intensity is set up, and 2 are pits that central boss 4 and combustion chamber wall surface form.Be perforated plate type atomizer 11 above central boss, oil nozzle is provided with center nozzle opening 12 and side direction nozzle opening 10.The diameter of center nozzle opening is 0.15～0.25mm, and the dead in line of axis and oil nozzle 11 and piston.Form taper from the oil bundle of central nozzle opening ejection, the cone-apex angle of this cone angle will cooperatively interact with the distance of center of orifices 12 and central boss 4 end faces, guarantees that this part oily bundle can all strike the boss end face.Nozzle opening 10 has 4～6, and diameter is 0.33～0.36mm, and their axis is all on the conical surface of an imaginary cone.The angle Selection of the cone-apex angle of this taper will guarantee piston when the top dead center of compression stroke, and the oil bundle 9 of ejection can strike on the combustion chamber wall surface of guiding circular arc 8 tops from nozzle opening 10.Spray orifice 10 is 25～40mm to the distance of rum point.
The working procedure of native system is such: near compression stroke top dead center, fuel oil is sprayed in the cylinder.At first strike on the flat-top boss of bottom, firing chamber from the fuel oil of central spray orifice 12 ejections, will form a discoid spray 4.And entrainment air from upper and lower surface, make full use of near the air in space, boss top.Because this part fuel oil central collision boss, so the loss of momentum is big.The penetration distance of fuel oil is shorter after being rebuffed, and mixture strength is bigger, point of ignition will at first occur.From around the fuel oil of spray orifice 12 ejection, behind the bump sidewall, come off from wall along locating in current limliting, form a large amount of thin combustible gases 3 at space secondary-atomizing and air mixing.Because the diameter of side direction spray orifice is bigger, and injection pressure is lower, so the diameter of elaioleucite is also bigger in the spray of secondary injection, needs regular hour and air mixing point of ignition could occur.And occurring before the point of ignition, piston 14 has begun descending.Under the effect of reverse crowded stream, the flame of centre of Chu Xianing will at first heat nearest side direction mixed gas at first, make it to accelerate evaporation and take fire, and move to cylinder cap 15 bottoms while burning, and light adjacent mixed gas simultaneously.The inflammable mixture of middle and lower part, firing chamber will hierarchically identify oneself with in the burning in uphill process and go like this.Ideal situation is that flame can stop the long time in piston crater.When cold wall is run in the space that mixed gas rises to piston top, burnt fully like this, thereby reduced the discharge amount of HC.Whole combustion process will can think to have had most of feature that HCCI burns based on the premix burning.In addition, by optimizing the useful area ratio of central spray orifice and side direction spray orifice, wish when high load, to be unlikely to make that the air fuel ratio of side direction spray place is too small and the discharge amount of PM is increased.And, therefore have the long time to participate in burning because central authorities' spraying takes fire at first.PM that rich mixture burning herein generates and CO etc., can be in uphill process and the air of firing chamber oral area and firing chamber upper space reflect once more and oxidize away.Thereby make this combustion system can under diesel engine high load operating mode, keep better economic characteristic and emission performance.
Claims (4)
1. combustion system of directly jetting diesel engine, it is characterized in that, mainly comprise cylinder (13), cylinder head (15),, oil nozzle (11), piston (14) and firing chamber (1): described oil nozzle is provided with a plurality of nozzle openings, one of them (12) are positioned at oil nozzle front end central authorities, and just nozzle hole cone angle is 0, the central lines of the axis of this spray orifice and firing chamber taper; Other spray orifice (10) axis arranged on an imaginary conical surface, the center line of this conical surface center line and firing chamber taper and the dead in line of center of orifices, and the drift angle of this conical surface is 100 °～160 °; This system adopts the gas handling system of 4 valves, and requires oil nozzle just to put; In addition, the firing chamber bottom center that is adopted is a boss (5), and the last end face of this boss is the plane, also can be convex surface or concave surface; Wall is provided with the annular boss (7) that is formed by one section guiding circular arc (8) around the firing chamber.
2. combustion system of directly jetting diesel engine according to claim 1 is characterized in that, the diameter of described oil nozzle center of orifices (12) is 0.10～0.25mm, and the diameter of side direction spray orifice (10) is 0.30～0.40mm.
3. combustion system of directly jetting diesel engine according to claim 1 and 2, it is characterized in that, the radius of described transition arc (8) is 0.5～2.5mm, the status requirement of transition arc is when piston (14) compression stroke top dead center, and the oil bundle that sprays from oil nozzle side direction spray orifice can strike on firing chamber (1) wall of circular arc top.
4. combustion system of directly jetting diesel engine according to claim 3, it is characterized in that, the end face of described bottom boss (5) has 10～20mm to the distance of oil nozzle (11) in injection process, and the area of boss end face will guarantee that the oily Shu Douneng structure of center of orifices (12) ejection strikes top face.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNA2004100023654A CN1556313A (en) | 2004-01-06 | 2004-01-06 | Direct spraying type diesel engine combustion system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNA2004100023654A CN1556313A (en) | 2004-01-06 | 2004-01-06 | Direct spraying type diesel engine combustion system |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN1556313A true CN1556313A (en) | 2004-12-22 |
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ID=34350710
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNA2004100023654A Pending CN1556313A (en) | 2004-01-06 | 2004-01-06 | Direct spraying type diesel engine combustion system |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN1556313A (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101793206A (en) * | 2010-03-17 | 2010-08-04 | 大连理工大学 | Direction-injection diesel engine combustion chamber |
| CN104632353B (en) * | 2014-12-26 | 2018-06-05 | 江苏大学 | A kind of diesel engine with direct injection collision atomization diffusion combustion system |
-
2004
- 2004-01-06 CN CNA2004100023654A patent/CN1556313A/en active Pending
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101793206A (en) * | 2010-03-17 | 2010-08-04 | 大连理工大学 | Direction-injection diesel engine combustion chamber |
| CN101793206B (en) * | 2010-03-17 | 2011-07-20 | 大连理工大学 | Direction-injection diesel engine combustion chamber |
| CN104632353B (en) * | 2014-12-26 | 2018-06-05 | 江苏大学 | A kind of diesel engine with direct injection collision atomization diffusion combustion system |
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| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C02 | Deemed withdrawal of patent application after publication (patent law 2001) | ||
| WD01 | Invention patent application deemed withdrawn after publication |