CN108412603B - Piston combustion chamber structure - Google Patents
Piston combustion chamber structure Download PDFInfo
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- CN108412603B CN108412603B CN201810381005.1A CN201810381005A CN108412603B CN 108412603 B CN108412603 B CN 108412603B CN 201810381005 A CN201810381005 A CN 201810381005A CN 108412603 B CN108412603 B CN 108412603B
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- combustion chamber
- omega
- shaped combustion
- piston
- oil
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- 238000002485 combustion reaction Methods 0.000 title claims abstract description 137
- 239000000446 fuel Substances 0.000 claims description 16
- 230000007704 transition Effects 0.000 claims description 4
- 239000003921 oil Substances 0.000 abstract description 42
- 239000000295 fuel oil Substances 0.000 abstract description 5
- 239000002245 particle Substances 0.000 abstract description 5
- 230000000694 effects Effects 0.000 abstract description 2
- MWUXSHHQAYIFBG-UHFFFAOYSA-N nitrogen oxide Inorganic materials O=[N] MWUXSHHQAYIFBG-UHFFFAOYSA-N 0.000 abstract 3
- 230000006872 improvement Effects 0.000 description 5
- 230000009471 action Effects 0.000 description 3
- 239000000243 solution Substances 0.000 description 3
- 239000007789 gas Substances 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 230000008646 thermal stress Effects 0.000 description 2
- 241000282414 Homo sapiens Species 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 238000005336 cracking Methods 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 238000013461 design Methods 0.000 description 1
- 238000011161 development Methods 0.000 description 1
- 238000002347 injection Methods 0.000 description 1
- 239000007924 injection Substances 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
- 239000003595 mist Substances 0.000 description 1
- 239000000126 substance Substances 0.000 description 1
- 238000012360 testing method Methods 0.000 description 1
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B23/00—Other engines characterised by special shape or construction of combustion chambers to improve operation
- F02B23/02—Other engines characterised by special shape or construction of combustion chambers to improve operation with compression ignition
- F02B23/06—Other engines characterised by special shape or construction of combustion chambers to improve operation with compression ignition the combustion space being arranged in working piston
- F02B23/0672—Omega-piston bowl, i.e. the combustion space having a central projection pointing towards the cylinder head and the surrounding wall being inclined towards the cylinder center axis
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
- F02F3/00—Pistons
- F02F3/26—Pistons having combustion chamber in piston head
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
- F02M61/14—Arrangements of injectors with respect to engines; Mounting of injectors
-
- 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
Abstract
The invention relates to the technical scheme and the structural field of internal combustion engines, in particular to a piston combustion chamber structure, which comprises an upper shallow basin-shaped combustion chamber and a lower omega-shaped combustion chamber, wherein the upper shallow basin-shaped combustion chamber and the lower omega-shaped combustion chamber are combined through the position of an oil injector and the position of an oil line, the shallow basin-shaped combustion chamber is transited to the omega-shaped combustion chamber by a conical surface beta angle, an orifice of the omega-shaped combustion chamber is connected with the shallow basin-shaped combustion chamber by a conical surface delta angle, a transitional area between the orifice of the omega-shaped combustion chamber and the shallow basin-shaped combustion chamber is closed, and the distance h between the oil beam center of the oil injector and the top surface of a piston is controlled to be 1.1-1.5 mm. The smart combination of the shallow-basin-type combustion chamber and the omega-type combustion chamber plays the advantages and merits of the shallow-basin-type combustion chamber and the omega-type combustion chamber. The invention achieves the expected mixing effect and requirement between the fuel oil entering the cylinder and the fresh air entering the cylinder, so as to control the combustion speed and temperature and control the emission of nitrogen oxides and PM particles.
Description
Technical Field
The invention relates to a novel piston combustion chamber technical scheme, which is used for the structural design of a piston combustion chamber of a diesel engine with emission regulations of five countries and above, is matched with an oil sprayer, belongs to the technical scheme and the structural field of internal combustion engines, and particularly relates to a piston combustion chamber structure.
Background
In recent years, performance indexes are continuously enhanced due to the improvement of the technical level of the engine, reliability is improved, and emission requirements are becoming more stringent. Mixing and burning of fuel oil and fresh impulse directly affects various aspects of emission, performance, fuel consumption, noise and reliability of the engine.
With the development and progress of society, the requirements of human beings on living environment and air quality are higher and higher, the national regulations on the air quality are becoming stricter, and the requirements on the emission index and the economical efficiency of an internal combustion engine are higher and higher. The technology of internal combustion engines is also continuously developed, and the power rise of the engines is also continuously improved, so that serious tests are provided for the emission, reliability, noise requirements and later maintenance of the engines. Pistons are important moving parts of an engine, are basic components of the engine, and the pistons and combustion chambers thereof directly affect the emissions, life, economy and noise levels of the engine.
Most engine piston combustors employ omega combustors, which suffer from the disadvantage: the air inflow vortex is strong, the fuel oil bundles sprayed out by the fuel injector are unevenly mixed with fresh air in a short time, the combustion is insufficient, the combustion is not easy to control in a certain range, the emission of NOx, PM and the like is increased, and the fuel consumption is increased. The omega-shaped combustion chamber orifice has abrupt shape change and is in a high-temperature area for ignition combustion, so that the piston omega-shaped combustion chamber orifice is easy to crack locally.
Disclosure of Invention
The invention aims to overcome the defects in the prior art and provides a piston combustion chamber structure, which is characterized by comprising a piston, an upper shallow basin-shaped combustion chamber and a lower omega-shaped combustion chamber, wherein the piston and the upper shallow basin-shaped combustion chamber are combined through the positions of an oil injector and an oil line,
the shallow-basin-shaped combustion chamber is transited to the omega-shaped combustion chamber by the angle of the conical surface beta, the orifice of the omega-shaped combustion chamber is connected with the shallow-basin-shaped combustion chamber by the angle of the conical surface delta, the transition area between the orifice of the omega-shaped combustion chamber and the shallow-basin-shaped combustion chamber is closed, and the round angle is transited naturally; the distance h between the center of the oil beam of the oil sprayer and the top surface of the piston is controlled to be 1.1mm-1.5mm.
Further improvement of the scheme is that the diameters phi a and phi a of the orifices of the shallow basin-shaped combustion chamber are controlled to be 62 mm-66 mm, the round angles ra at the bottom of the combustion chamber are controlled to be 1mm-2mm, and the round angles rc of the orifices are controlled to be 0.1mm-0.5mm;
the diameter phi b of the orifice of the omega-shaped combustion chamber is controlled to be 50 mm-53 mm, and the distance H2 from the orifice of the omega-shaped combustion chamber to the top surface of the piston is controlled to be 4.5mm-6.5mm; the bottom fillet rb of the combustion chamber is 5mm-7mm;
the ratio of omega combustion chamber orifice diameter Φb to shallow basin combustion chamber orifice diameter Φa is 78% -82%.
Further improvement of the scheme is that the diameter phi c of the bottom of the omega-shaped combustion chamber is controlled to be phi 52 mm-phi 56mm; the depth H1 is 14mm-18mm;
the diameter ratio phi b/phi c of the orifice diameter phi b of the omega-type combustion chamber to the bottom diameter phi c of the omega-type combustion chamber is controlled to be 93-96%; delta is 22-25 DEG
The cone angle gamma of the boss top of the omega-shaped combustion chamber is 117-120 degrees, and the distance H3 between the boss top and the top surface of the piston is 4.5-6.5 mm.
The scheme is further improved, the distance h between the center of the oil beam of the oil injector and the top surface of the piston is taken as the z-axis coordinate direction, the intersection point of the center of the cylinder hole and the center of the crankshaft is taken as a plane datum point, and the M, N line is the vertical and horizontal symmetrical center line in the top view of the piston; line P, Q is the vertical and horizontal center line of symmetry in the top view of the combustion chamber; the W point is a projection point of the oil beam center of the oil sprayer in a piston top view, the x-axis offset of the oil beam center at the intersection point of P, Q lines is a, the y-axis offset is b, a is 3.5mm-4.5mm, and b is 0.8mm-1.2mm.
The scheme is further improved, and the height H of a drop point of a fuel line of the fuel injector is 5mm-7mm; the length L of the oil line is controlled to be 21mm-24mm; the included angle alpha of the fuel injector is 78-80 degrees.
The invention has the following advantages:
the invention is the ingenious combination of the shallow-basin-shaped combustion chamber and the omega-shaped combustion chamber, and plays the advantages and merits of the shallow-basin-shaped combustion chamber and the omega-shaped combustion chamber. The diameter phi of the port of the shallow basin-shaped combustion chamber is 62 mm-phi 66mm, so that mixing and uneven combustion caused by oil bundles to the cylinder wall and the top surface of the piston are avoided, the emission value of NOx and PM (particles) is increased, the rounded angle at the top is 0.1mm-0.5mm, the rounded angle at the orifice of the combustion chamber is 0.1mm-0.5mm, the rounded angle at the bottom is 1mm-2mm, the thermal stress is reduced, cracking of the top of the piston is avoided, vortex can be formed locally, and mixing and combustion between fuel oil injected into the cylinder and fresh air entering the cylinder are facilitated.
The invention has the advantages that the ratio of the diameter of the orifice of the omega combustion chamber to the diameter of the orifice of the shallow basin-shaped combustion chamber is 78-82 percent, and the ratio of the diameter of the orifice of the omega combustion chamber to the diameter of the bottom is 93-96 percent, so as to control the intensity of air inlet vortex, ensure that the fuel oil entering the cylinder and the fresh air entering the cylinder reach the expected mixing effect and requirement, control the combustion speed and temperature, and control the emission of NOx and PM (particles).
The oil line drop point of the oil sprayer is controlled in an omega combustion chamber, the cone angle of the inner cavity of the omega combustion chamber is 117-120 degrees according to the position of the top surface of the piston at 5-7 mm, the oil line drop point is matched with the oil sprayer, the depth of the omega combustion chamber is 14-18 mm, and the bottom of the omega combustion chamber is transited by a round angle of 5-7 mm. The combustion chamber, the oil line position, the drop point and the air inlet vortex are effectively combined, under the action of the air inlet vortex, the oil beam and the fresh air in the combustion chamber are uniformly mixed and combusted, the emission of NOx and PM (particulate matters) is effectively controlled, and the fuel consumption and the combustion noise are reduced.
Drawings
Fig. 1 is a front view of the present invention.
Fig. 2 is a top view of the piston top surface.
Fig. 3 is a cross-sectional view A-A of fig. 2.
Detailed Description
The invention will be further described with reference to the accompanying drawings.
1-3, a piston combustion chamber structure is provided, which is characterized by comprising a piston 1, wherein the center line of the piston is shown in FIG. 1, and an upper shallow basin-shaped combustion chamber 2 is arranged at the upper part of the piston, and the piston moves upwards to the vicinity of a top dead center to prevent oil injection from splashing to the cylinder wall and the top surface of the piston; the upper part is a shallow-basin-shaped combustion chamber, and when in an air inlet stroke, tumble flows are formed around the shallow-basin-shaped combustion chamber, so that mixing and combustion are facilitated, and thermal stress is effectively avoided due to the orifice of the shallow-basin-shaped combustion chamber and the round corner R at the bottom.
A lower omega-type combustion chamber 4, which is combined with the position of the oil line by the position of the oil injector 3, wherein the center line of the oil injector is shown as the center line of the oil injector in figure 1;
the upper and lower combustion chambers share a centerline, as shown by the combustion chamber centerline in FIG. 1;
the shallow-basin-shaped combustion chamber 2 is transited to the omega-shaped combustion chamber at a conical surface beta angle, the orifice of the omega-shaped combustion chamber 4 is connected with the shallow-basin-shaped combustion chamber 2 at a conical surface delta angle, the transition area between the orifice and the shallow-basin-shaped combustion chamber is closed, and the round angle is transited naturally; the flow speed of the gas is increased, stronger vortex is formed, the mixing and the full combustion are enhanced, the emission of PM (particles), NOx and the like in the combustion process is reduced, and the fuel consumption is reduced;
the distance between the center of the oil beam of the oil sprayer and the top surface of the piston 1 is controlled to be 1.1mm-1.5mm.
The important size of the piston combustion chamber is corresponding to and matched with the position of the oil line falling point of the oil injector, and is matched with the air inlet vortex of the air inlet channel, so that stronger vortex is formed, and the mixing and the combustion are enhanced.
Specifically, the diameter phi a of an orifice of the shallow basin-shaped combustion chamber 2 is controlled to be 62 mm-66 mm, the round angle ra at the bottom of the combustion chamber is controlled to be 1mm-2mm, and the round angle rc of the orifice is controlled to be 0.1mm-0.5mm;
the diameter phi b of the orifice of the omega-shaped combustion chamber 4 is controlled to be 50 mm-53 mm, and the distance H2 from the orifice of the omega-shaped combustion chamber to the top surface of the piston is controlled to be 4.5mm-6.5mm; the bottom fillet rb of the combustion chamber is 5mm-7mm;
the bottom of the shallow basin-shaped combustion chamber 2 is smoothly transited to the lower omega-shaped combustion chamber 4 by a beta angle conical surface, and the beta angle is 24-27 degrees;
the orifice of the omega-shaped combustion chamber 4 is connected with the bottom of the shallow-basin-shaped combustion chamber 2 in a smooth transition manner by a delta angle conical surface, wherein the delta angle is 22-25 degrees;
the ratio of omega combustion chamber orifice diameter Φb to shallow basin combustion chamber orifice diameter Φa is 78% -82%. The proper vortex strength is formed, so that the oil mist and fresh air are effectively mixed, the combustion rate is controlled to a certain extent, and the emission values of harmful substances PM particles and harmful gases NOx are reduced;
further improvement of the scheme is that the diameter phi c of the bottom of the omega-shaped combustion chamber 4 is controlled to be phi 52 mm-phi 56mm; the depth H1 is 14mm-18mm;
the diameter ratio phi b/phi c of the orifice diameter phi b of the omega-shaped combustion chamber 4 to the bottom diameter phi c of the omega-shaped combustion chamber 4 is controlled to be 93-96%; delta is 22-25 DEG
The cone angle gamma of the boss top of the omega-shaped combustion chamber is 117-120 degrees, and the distance H3 between the boss top and the top surface of the piston 1 is 4.5-6.5 mm.
As shown in fig. 2, a top view of the top surface of the piston is shown, wherein the distance h from the center of the oil beam of the oil injector to the top surface of the piston 1 is taken as the z-axis coordinate direction, the intersection point of the center of the cylinder hole and the center of the crankshaft is taken as a plane datum point, and a M, N line is taken as a vertical and horizontal symmetrical center line in the top view of the piston; line P, Q is the vertical and horizontal center line of symmetry in the top view of the combustion chamber. The W point is a projection point of the oil beam center of the oil sprayer in a piston top view, the X-axis offset of the projection point W at the P, Q line intersection point is a, the y-axis offset is b, a is 3.5mm-4.5mm, and b is 0.8mm-1.2mm. The intersection point coordinates (c, d) of P, Q lines of the combustion chamber center may be different according to different models.
Further improvements to the above-described arrangements, the placement and matching of the combustion chamber and the injector location. Is the key for realizing the performance index of the engine and meeting the emission limit value.
Specifically, the height H of the oil line drop point of the oil sprayer 3 is 5mm-7mm; the length L of the oil line is controlled to be 21mm-24mm; the included angle alpha of the fuel injector is 78-80 degrees.
The scheme is further improved, and the combustion chamber, the oil beam arrangement of the oil injector and the air inlet vortex are matched and combined. Under the action of air inlet vortex, the oil beam and fresh air in the combustion chamber are uniformly mixed and combusted, so that the emission of NOx and PM (particulate matters) is effectively controlled, and the fuel consumption and the combustion noise are reduced.
In the invention, the positions of the fuel injectors are directly related to the positions and the drop points of the fuel lines, the length of each fuel line and the chord length among the fuel lines are basically equal, and under the action of air inlet vortex, the uniform mixing, ignition and combustion of injected fuel and air are ensured, and the NOx emission and PM emission are effectively reduced.
Finally, it should be noted that the above-mentioned embodiments are only for illustrating the technical solution of the present invention, and not for limiting the same, and although the present invention has been described in detail with reference to examples, it should be understood by those skilled in the art that modifications and equivalents may be made to the technical solution of the present invention without departing from the spirit and scope of the technical solution of the present invention, and all such modifications and equivalents are intended to be encompassed in the scope of the claims of the present invention.
Claims (3)
1. The piston combustion chamber structure is characterized by comprising a piston (1), an upper shallow basin-shaped combustion chamber (2) and a lower omega-shaped combustion chamber (4), wherein the piston and the upper shallow basin-shaped combustion chamber are combined through the position of an oil injector (3) and the position of an oil line;
the shallow-basin-shaped combustion chamber (2) is transited to the omega-shaped combustion chamber at a conical surface beta angle, the orifice of the omega-shaped combustion chamber (4) is connected with the shallow-basin-shaped combustion chamber (2) at a conical surface delta angle, the transition area between the orifice and the orifice is closed, and the round angle is transited naturally; the distance h between the center of the oil beam of the oil sprayer and the top surface of the piston (1) is controlled to be 1.1mm-1.5mm;
taking the distance h between the center of the oil beam of the oil sprayer and the top surface of the piston (1) as the z-axis coordinate direction, taking the intersection point of the center of the cylinder hole and the center of the crankshaft as a plane datum point, and taking a M, N line as a vertical and horizontal symmetrical center line in the top view of the piston; line P, Q is the vertical and horizontal center line of symmetry in the top view of the combustion chamber; the W point is a projection point of the oil beam center of the oil sprayer in a top view of the piston, the offset of an x axis of the oil beam center positioned at a P, Q line intersection point is a, the offset of a y axis is b, a is 3.5mm-4.5mm, and b is 0.8mm-1.2mm;
the height H of the oil line falling point of the oil sprayer (3) is 5mm-7mm; the length L of the oil line is controlled to be 21mm-24mm; the included angle alpha of the fuel injector is 78-80 degrees.
2. The piston combustion chamber structure of claim 1, wherein:
the diameter phi a of an orifice of the shallow basin-shaped combustion chamber (2) is controlled to be 62 mm-66 mm, the round angle ra at the bottom of the combustion chamber is controlled to be 1mm-2mm, and the round angle rc of the orifice is controlled to be 0.1mm-0.5mm;
the diameter phi b of the orifice of the omega-shaped combustion chamber (4) is controlled to be 50 mm-53 mm, and the distance H2 from the orifice of the omega-shaped combustion chamber to the top surface of the piston is controlled to be 4.5mm-6.5mm; the bottom fillet rb of the combustion chamber is 5mm-7mm;
the bottom of the shallow basin-shaped combustion chamber (2) is smoothly transited to the lower omega-shaped combustion chamber (4) by a beta angle conical surface, and the beta angle is 24-27 degrees;
the ratio of omega combustion chamber orifice diameter Φb to shallow basin combustion chamber orifice diameter Φa is 78% -82%.
3. The piston combustion chamber structure of claim 1, wherein: the diameter phi c of the bottom of the omega-shaped combustion chamber (4) is controlled to be phi 52 mm-phi 56mm; the depth H1 is 14mm-18mm;
the diameter ratio phi b/phi c of the orifice diameter phi b of the omega-shaped combustion chamber (4) to the bottom diameter phi c of the omega-shaped combustion chamber (4) is controlled to be 93-96 percent, and the angle delta is 22-25 degrees;
the cone angle gamma of the boss top of the omega-shaped combustion chamber is 117 degrees to 120 degrees, and the distance H3 between the boss top and the top surface of the piston (1) is 4.5mm to 6.5mm.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810381005.1A CN108412603B (en) | 2018-04-25 | 2018-04-25 | Piston combustion chamber structure |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810381005.1A CN108412603B (en) | 2018-04-25 | 2018-04-25 | Piston combustion chamber structure |
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| Publication Number | Publication Date |
|---|---|
| CN108412603A CN108412603A (en) | 2018-08-17 |
| CN108412603B true CN108412603B (en) | 2023-12-05 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201810381005.1A Active CN108412603B (en) | 2018-04-25 | 2018-04-25 | Piston combustion chamber structure |
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| CN (1) | CN108412603B (en) |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111894727A (en) * | 2020-06-29 | 2020-11-06 | 东风商用车有限公司 | Four-valve direct-injection diesel engine combustion chamber |
| CN113090379A (en) * | 2021-04-29 | 2021-07-09 | 广西玉柴机器股份有限公司 | Layered gas engine combustion chamber and vortex rotation center processing method |
| CN114320641B (en) * | 2022-03-11 | 2022-06-21 | 潍柴动力股份有限公司 | Engine combustion system, control method and engine |
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| EP1643098A1 (en) * | 2004-10-04 | 2006-04-05 | Renault s.a.s. | Off-centered fuel injection nozzle for automotive combustion engine |
| CN101160459A (en) * | 2005-04-19 | 2008-04-09 | 洋马株式会社 | Direct injection diesel engine |
| CN101984232A (en) * | 2010-11-08 | 2011-03-09 | 东风朝阳柴油机有限责任公司 | Diesel combustion chamber of rotary structure |
| CN201786475U (en) * | 2010-08-03 | 2011-04-06 | 奇瑞汽车股份有限公司 | Head structure of piston for diesel engine |
| CN201843693U (en) * | 2010-06-07 | 2011-05-25 | 安徽省恒泰活塞制造有限公司 | Piston combustion chamber for air-cooled single-cylinder diesel engine with small cylinder diameter |
| CN202194718U (en) * | 2011-08-04 | 2012-04-18 | 安徽全柴动力股份有限公司 | Combustor chamber of diesel engine capable of satisfying homogeneous charge compression ignition |
| CN105909420A (en) * | 2016-06-14 | 2016-08-31 | 广西玉柴机器股份有限公司 | Combustion chamber capable of reducing soot in diesel engine cylinder |
| CN208184837U (en) * | 2018-04-25 | 2018-12-04 | 江苏四达动力机械集团有限公司 | Piston combustion chamber structure |
-
2018
- 2018-04-25 CN CN201810381005.1A patent/CN108412603B/en active Active
Patent Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP1643098A1 (en) * | 2004-10-04 | 2006-04-05 | Renault s.a.s. | Off-centered fuel injection nozzle for automotive combustion engine |
| CN101160459A (en) * | 2005-04-19 | 2008-04-09 | 洋马株式会社 | Direct injection diesel engine |
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| CN108412603A (en) | 2018-08-17 |
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