CN113882938B - Spiral vortex precombustion chamber ignition system - Google Patents
Spiral vortex precombustion chamber ignition system Download PDFInfo
- Publication number
- CN113882938B CN113882938B CN202111142276.XA CN202111142276A CN113882938B CN 113882938 B CN113882938 B CN 113882938B CN 202111142276 A CN202111142276 A CN 202111142276A CN 113882938 B CN113882938 B CN 113882938B
- Authority
- CN
- China
- Prior art keywords
- combustion chamber
- prechamber
- wall
- flame
- ignition system
- 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.)
- Active
Links
- 238000002485 combustion reaction Methods 0.000 claims abstract description 139
- 238000011161 development Methods 0.000 claims abstract description 20
- 238000000034 method Methods 0.000 claims abstract description 7
- 239000007789 gas Substances 0.000 claims description 94
- 239000000203 mixture Substances 0.000 claims description 61
- 239000000446 fuel Substances 0.000 claims description 17
- 230000033001 locomotion Effects 0.000 claims description 9
- IJGRMHOSHXDMSA-UHFFFAOYSA-N Atomic nitrogen Chemical compound N#N IJGRMHOSHXDMSA-UHFFFAOYSA-N 0.000 claims description 8
- CURLTUGMZLYLDI-UHFFFAOYSA-N Carbon dioxide Chemical compound O=C=O CURLTUGMZLYLDI-UHFFFAOYSA-N 0.000 claims description 8
- LFQSCWFLJHTTHZ-UHFFFAOYSA-N Ethanol Chemical compound CCO LFQSCWFLJHTTHZ-UHFFFAOYSA-N 0.000 claims description 6
- QVGXLLKOCUKJST-UHFFFAOYSA-N atomic oxygen Chemical compound [O] QVGXLLKOCUKJST-UHFFFAOYSA-N 0.000 claims description 6
- 230000008859 change Effects 0.000 claims description 6
- VNWKTOKETHGBQD-UHFFFAOYSA-N methane Chemical compound C VNWKTOKETHGBQD-UHFFFAOYSA-N 0.000 claims description 6
- 239000001301 oxygen Substances 0.000 claims description 6
- 229910052760 oxygen Inorganic materials 0.000 claims description 6
- 239000001569 carbon dioxide Substances 0.000 claims description 4
- 229910002092 carbon dioxide Inorganic materials 0.000 claims description 4
- 150000001875 compounds Chemical class 0.000 claims description 4
- 229910052757 nitrogen Inorganic materials 0.000 claims description 4
- 230000009471 action Effects 0.000 claims description 3
- 230000006835 compression Effects 0.000 claims description 3
- 238000007906 compression Methods 0.000 claims description 3
- 239000008240 homogeneous mixture Substances 0.000 claims description 3
- 239000003345 natural gas Substances 0.000 claims description 3
- 230000002093 peripheral effect Effects 0.000 claims description 3
- 239000000126 substance Substances 0.000 claims description 3
- 238000004891 communication Methods 0.000 claims description 2
- 230000000630 rising effect Effects 0.000 claims description 2
- 238000010586 diagram Methods 0.000 description 4
- 238000005516 engineering process Methods 0.000 description 4
- MWUXSHHQAYIFBG-UHFFFAOYSA-N Nitric oxide Chemical compound O=[N] MWUXSHHQAYIFBG-UHFFFAOYSA-N 0.000 description 3
- 230000007423 decrease Effects 0.000 description 3
- 230000000694 effects Effects 0.000 description 3
- 238000002347 injection Methods 0.000 description 3
- 239000007924 injection Substances 0.000 description 3
- 238000004519 manufacturing process Methods 0.000 description 3
- 230000002411 adverse Effects 0.000 description 2
- 239000003054 catalyst Substances 0.000 description 2
- -1 concentration Substances 0.000 description 2
- 240000008042 Zea mays Species 0.000 description 1
- 235000005824 Zea mays ssp. parviglumis Nutrition 0.000 description 1
- 235000002017 Zea mays subsp mays Nutrition 0.000 description 1
- 230000001133 acceleration Effects 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000008901 benefit Effects 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 235000008429 bread Nutrition 0.000 description 1
- 235000005822 corn Nutrition 0.000 description 1
- 230000003247 decreasing effect Effects 0.000 description 1
- 230000006872 improvement Effects 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 238000012545 processing Methods 0.000 description 1
- 230000001737 promoting effect Effects 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
- 238000011160 research Methods 0.000 description 1
- 239000002912 waste gas Substances 0.000 description 1
Classifications
-
- 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
- F02B19/00—Engines characterised by precombustion chambers
- F02B19/08—Engines characterised by precombustion chambers the chamber being of air-swirl type
-
- 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
- F02B19/00—Engines characterised by precombustion chambers
- F02B19/10—Engines characterised by precombustion chambers with fuel introduced partly into pre-combustion chamber, and partly into cylinder
- F02B19/1019—Engines characterised by precombustion chambers with fuel introduced partly into pre-combustion chamber, and partly into cylinder with only one pre-combustion chamber
-
- 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
- F02B19/00—Engines characterised by precombustion chambers
- F02B19/12—Engines characterised by precombustion chambers with positive ignition
-
- 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
- F02B19/00—Engines characterised by precombustion chambers
- F02B19/16—Chamber shapes or constructions not specific to sub-groups F02B19/02 - F02B19/10
-
- 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
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Combustion Methods Of Internal-Combustion Engines (AREA)
Abstract
The invention provides a spiral vortex precombustor ignition system, which comprises a precombustor (1), a spark plug (2), a jet valve (3), a main combustion chamber (4), at least an air inlet hole (5) and at least a jet hole (6); the precombustion chamber (1) is arranged in a cylinder cover (8) above the main combustion chamber (4) near the center of the cylinder (7); the main combustion chamber (4) is composed of a cylinder (7), a lower bottom surface of a cylinder cover (8) and a top surface of a piston (15); the prechamber (1) has an upper space (11) and a lower space (12); the ignition system establishes a high pressure difference between a main combustion chamber and a precombustion chamber in the process of air intake of the precombustion chamber, so that high-speed air intake flow is generated, and a spiral vortex model is established; the model ensures that the generation, growth and flame development of the flame kernel are fully ensured, solves the problems of stability, controllability and robustness of ignition of the lean-charge precombustor, and prevents the occurrence of pre-ignition and flameout events.
Description
Technical Field
The invention relates to an ignition technology of an internal combustion engine, in particular to an ignition technology for igniting a lean mixture in a precombustion chamber by a spark plug, and the ignition technology is used for finally igniting the lean main mixture by high-temperature high-speed injection of high-pressure gas generated by combustion of the lean mixture in the precombustion chamber into a main combustion chamber.
Background
The pre-combustion chamber ignition can obviously shorten the combustion duration of the mixed gas in the main combustion chamber, can ignite the lean mixed gas, reduce the combustion temperature, reduce the emission of NOx, improve the combustion efficiency and reduce the oil consumption of the internal combustion engine, and is a main reason for developing research on the internal combustion engine worldwide.
The ignition of the precombustion chamber refers to that a spark plug is adopted in the precombustion chamber of the internal combustion engine to ignite the pilot mixed gas, and high-temperature and high-pressure gas is formed into jet gas through a channel between the precombustion chamber and the main combustion chamber, and the jet gas is sprayed into the main combustion chamber through a jet hole to ignite the mixed gas in the main combustion chamber. The pre-combustion chamber ignition comprises an active pre-combustion chamber and a passive pre-combustion chamber ignition, wherein the active pre-combustion chamber refers to that mixed gas in the pre-combustion chamber is fed from the outside of the internal combustion engine through an independent pipeline; the passive precombustion chamber means that the mixture in the precombustion chamber is pressed in by the piston from the main combustion chamber.
Referring to lean mixture, there are mainly two states: one type of mixture is a much higher stoichiometric air/fuel ratio with an excess air ratio lambda much greater than 1, which is an oxygen-enriched combustion that produces NOx compounds that require complex and expensive aftertreatment systems. The other mixture is equal to the theoretical air/fuel ratio with an excess air ratio lambda constantly equal to 1, but with the addition of more burnt gas, which is added to the mixture via an Exhaust Gas Recirculation (EGR). The NOx produced by it can be treated by low cost three way catalysts which are currently in great use.
For a passive prechamber, the composition, concentration, gas flow rate, gas flow direction, temperature, pressure, etc. of the pilot mixture entering the prechamber are affected by the composition, concentration, gas flow rate, gas flow direction, temperature, and pressure of the main mixture. In order to increase the efficiency of the internal combustion engine, it is desirable to use lean gas combustion to perform work, which has the advantage of greatly reducing the heat loss of the internal combustion engine. But difficulties follow: firstly, the gas in the main combustion chamber is thin, the consistency of the fuel concentration near the spark plug is difficult to achieve, the spark plug is difficult to effectively ignite the mixed gas, and stable fire nuclei are generated. Secondly, the space of the main combustion chamber is larger, and air inlet vortex and tumble formed by the shape of an air passage and an air inlet valve are broken near the upper dead center, so that the flowing direction and the flowing speed of the mixed gas are subjected to uncertainty change, and the generated fire nuclei are difficult to grow and develop in a specific mode. Third, as the lean degree deepens, the combustion speed of the main mixture is greatly reduced, and large combustion cycle fluctuation is easy to form.
Briefly stated, the prechamber lean mixture ignition technique suffers from difficulties in both: formation of a core, growth of a core, development of a core, injection of energy of sufficiently high enthalpy into the main combustion chamber, acceleration of lean mixture to complete combustion, and the like.
Therefore, it is desirable to provide a method for igniting a lean pilot gas, which is capable of promoting the growth and development of a flame kernel in a specific mode after the flame kernel is generated, smoothly completing the combustion of the lean gas in the precombustion chamber, and generating the high-temperature and high-pressure gas in the precombustion chamber to perform jet ignition on the lean gas in the main combustion chamber, so as to realize the ignition and combustion of the lean gas in the main combustion chamber.
Disclosure of Invention
The present invention provides a helical vortex prechamber ignition system that attempts to create a stable helical vortex model in the prechamber that provides adequate assurance of flame kernel generation, growth, and flame development, thus addressing the stability, controllability, and robustness of prechamber ignition, particularly lean-charge prechamber ignition, preventing the occurrence of pre-ignition, flameout events, and reducing combustion cycle fluctuations.
The technical scheme of the invention is to provide a spiral vortex precombustor ignition system, which comprises a precombustor, a spark plug, a jet valve, a main combustion chamber, at least one air inlet hole and at least one jet hole; the precombustion chamber is arranged in a cylinder cover above the main combustion chamber near the center of the cylinder; the main combustion chamber consists of a cylinder, the bottom surface of the lower part of the cylinder cover and the top surface of the piston; the prechamber having an upper space and a lower space; the method is characterized in that:
the inner walls of the upper space and the lower space are in the shape of rotating bodies formed by rotating along the central axis of the precombustion chamber, the diameter phi of the inner wall of the upper space is gradually reduced from top to bottom and is connected with the diameter phi of the inner wall of the lower space, the diameter phi of the inner wall of the lower space is a fixed value or gradually reduced from top to bottom, the positive and negative electrodes of the spark plug are exposed in the upper space, the air inlet hole is arranged at the axial middle position of the lower space and is connected with the air inlet hole along the circumferential tangential direction of the inner wall of the lower space, and the air inlet hole can enable the main combustion chamber to be in gas communication with the precombustion chamber; the lower end face of the lower space is provided with a jet valve controlled by differential pressure, the jet hole is arranged near the periphery of the jet valve, and the jet hole can introduce the gas in the precombustion chamber into the main combustion chamber after the jet valve is opened;
the air flow is sprayed into the lower space of the precombustion chamber along the circumferential tangential direction of the inner wall of the lower space at a high speed, and a spiral vortex is formed in the lower space; the spiral vortex front rotates upwards and gradually decelerates from the inner wall circumference of the lower space gradually expanding to the upper space along a spiral lift angle until reaching the end face of an electrode of the spark plug, then the spiral vortex front reversely flows into the socket center and is converted into axial airflow from top to bottom, a spark position between the positive electrode and the negative electrode of the spark plug is arranged at the socket center, the downward flowing axial airflow is reduced along the diameter of the inner wall circumference, the flowing speed is accelerated, and on the way reaching the lower space, the axial airflow is continuously added into the spiral vortex on the periphery of the lower space to form a closed circumferential airflow motion model, namely a spiral vortex model, when the airflow is spirally upwards on the inner wall of the pre-combustion chamber and axially flows downwards from the socket center near the central axis of the pre-combustion chamber.
Further, in the pilot mixture of the spiral vortex model, all the gas components including carbon dioxide, oxygen and nitrogen, and the fuel are uniformly distributed, and constitute a homogeneous mixture.
Further, in the spiral vortex model, the air flow velocity distribution and the air flow movement direction distribution of the pilot mixture are stable and do not change due to the change of the rotating speed of the internal combustion engine.
Further, a fire core generation area F is arranged in the precombustion chamber, the fire core generation area F is a sphere, the sphere is positioned at the socket center of the spiral vortex model, the air flow speed of the socket center area is the lowest air flow speed area in the precombustion chamber, the air flow speed is not more than 15 m/s, the spark plug is ensured to successfully ignite the lean pilot gas mixture, and the fire core is successfully formed without being blown out by the air flow.
Further, a flame growth zone G is arranged in the precombustion chamber, the flame growth zone G is arranged below the flame generation zone F, in the flame growth zone G, the air flow speed is changed from slow speed to fast speed, the air flow is accelerated from 15 m/s close to the flame generation zone F to more than 80 m/s close to the lower space, the air flow is axially accelerated and downwards, the flame front of the flame is quickly guided to a larger area, the flame front of the flame is ensured not to be blown out by the air flow, and meanwhile, the flame is promoted to grow quickly.
Further, the area with the inner wall of the flame development area D in the precombustion chamber is the flame development area D; in the flame development zone D, as the diameter Φ of the inner wall of the upper space is reduced, the downward speed of the flame front is further increased, more airflow is wrapped up by the flame front and added into the high-speed vortex with the peripheral spiral rising, and at the moment, the airflow speed is up to 100 m/s to 1000 m/s, so that the flame front rapidly occupies the space of the whole precombustion chamber.
Further, the total flow area of the intake ports of the prechamber is numerically equal to 0.5% to 2% of the cylinder diameter; when the spark plug ignites, the pressure of the precombustion chamber of the spark plug is 25 to 50 percent of the pressure of the main combustion chamber; the high pressure differential of the main combustion chamber and the prechamber results in a high velocity of the intake air flow, which is 200 m/s to 1000 m/s.
Further, the total flow area of the jet holes is 3.5 to 6 times of the total flow area of the air inlet holes.
Further, jet-flow torches formed by jetting the precombustion chamber into the main combustion chamber are uniformly distributed in the space of the main combustion chamber, so that the main mixed gas is ignited at multiple points at the same time, and the combustion duration of the main mixed gas is shortened.
Further, the system is suitable for a mixture of two states: the first is that the mixture excess air ratio lambda is constant equal to, and the EGR rate is 0% to 50%; the second is or the mixture is a mixture with an excess air coefficient lambda far greater than 1.
Further, the wall of the prechamber is an integral part of the cylinder head, or of the spark plug housing, or of an intermediate part connected between the spark plug and the cylinder head.
Further, the shape of the inner wall of the upper space of the precombustion chamber is that the generatrix of the rotating body is an upward convex curve, and the rotation of the generatrix generates an upward convex curve; or the shape of the inner wall of the upper space of the precombustion chamber is that the generatrix of the rotating body is a downward convex curve, and the rotation of the generatrix generates a downward convex curve; or the upper space and the lower space of the precombustion chamber are combined into a whole, and the inner wall of the precombustion chamber is in an inverted cone shape with gradually reduced diameter; or the upper space of the precombustor is a cylinder with larger diameter, the lower space is a cylinder with smaller diameter, and the two cylinders are connected by an inverted cone to form an inner wall curved surface with a generatrix similar to a U-shaped shape.
Further, a spark plug is added to the cylinder facing the main combustion chamber for cold start and stable operation of the engine at low load.
Further, it can be used for single cylinder or in-line multi-cylinder internal combustion engines, as well as V-type, W-type, opposed-type or rotary internal combustion engines.
Further, the fuel used can be gasoline, natural gas, a mixture of gasoline and ethanol, and/or other substance fuel compounds or mixtures.
The invention has the beneficial effects that:
(1) The ignition system of the spiral vortex precombustion chamber is used for igniting and burning the lean mixture, so that the combustion temperature is reduced, the heat loss is reduced, the occurrence of a pre-ignition event is prevented, and the efficiency of the internal combustion engine is improved.
(2) By the spiral vortex model of the spiral vortex precombustor ignition system, the generation, growth and flame development of a flame kernel are fully ensured, so that the stability, controllability and robustness of precombustor ignition, particularly lean-charge precombustor ignition, are solved, flameout events are prevented, and combustion cycle fluctuation is reduced.
(3) The ability to resist knocking is improved by the helical swirl prechamber ignition system, which can increase the compression ratio of the internal combustion engine and further increase the efficiency of the internal combustion engine.
(4) The pre-chamber ignition system has little modification to the existing internal combustion engine, and thus has low development cost.
(5) The control system is rarely modified, the ECU of the original internal combustion engine can be used, and the electronic control system is convenient to modify.
(6) The improvement of the internal combustion engine occurs on the cylinder cover, but the cylinder cover production line only needs to be added with a spark plug hole processing procedure, the cost of the production line is low, and the production line is convenient to popularize.
(7) The oil consumption reduction expected by the technology of the invention can reach more than 15 percent.
(8) The fuel consumption is reduced, the combustion efficiency of the internal combustion engine can be improved, and the method has very important significance for improving the economy of the vehicle and reducing the carbon dioxide emission.
Drawings
FIG. 1 is a schematic diagram of a helical vortex prechamber ignition system according to the present invention;
FIG. 2 is a longitudinal cross-sectional view of a prechamber;
FIG. 3 is a cross-sectional view A-A of FIG. 2;
FIG. 4 is a schematic diagram of a spiral vortex model;
FIG. 5 is a section B-B of FIG. 4;
FIG. 6 is a schematic diagram of the distribution of the flame kernel generation zone, the flame kernel growth zone, and the flame development zone;
FIG. 7 is a schematic diagram of jet gas flow;
FIG. 8 is a cross-sectional view of the upper space of the prechamber in the shape of an upwardly convex curve;
FIG. 9 is a cross-sectional view of the upper space of the prechamber in the shape of a downwardly convex curve;
FIG. 10 is a cross-sectional view of the upper and lower volumes of the prechamber in the shape of an overall inverted cone;
FIG. 11 is a cross-sectional view of a prechamber upper space having a cylindrical shape.
Wherein:
1-a precombustion chamber; 2-spark plugs; 3-jet valves; 4-a main combustion chamber; 5-an air inlet hole; 6-jet holes; 7-cylinder; 8-a cylinder cover; 9-an upper space inner wall; 10-central axis of precombustor; 11-upper space; 12-lower space; 13-positive and negative electrodes; 14-inner wall of lower space; 15-a piston; 16-spiral vortex; 17-end face of spark plug electrode; 18-steamed corn bread; 19-axial airflow; 20-gas flow rate near the outer circumference; 21-gas flow rate near the inner circumference; 22-jet flare; 23-an upwardly convex curved surface; 24-a downward convex curved surface; 25-an inverted cone; f-a fire kernel generation region; g-a fire pit growth area; d-a flame development zone;
Detailed Description
Embodiments of the present invention will be described in detail below with reference to fig. 1 to 10.
Example 1:
as shown in fig. 1, this embodiment provides a helical swirl prechamber ignition system having a prechamber 1, a spark plug 2, a jet valve 3, a main combustion chamber 4, at least one inlet orifice 5, and at least one jet orifice 6. The prechamber 1 is arranged in a cylinder head 8 above the main combustion chamber 4 near the centre of the cylinder 7. The main combustion chamber 4 is formed by a cylinder 7, a lower bottom surface of a cylinder head 8 and a top surface of a piston 15.
As shown in fig. 2, the prechamber 1 has an upper space 11 and a lower space 12. The upper space inner wall 9 and the lower space inner wall 14 are shaped as rotating bodies rotating along the central axis 10 of the precombustor, the inner wall diameter phi of the upper space 11 gradually decreases from top to bottom and is connected with the inner wall diameter phi of the lower space 12, the inner wall diameter phi of the lower space 12 is a fixed value or gradually decreases from top to bottom, and the spark plug positive and negative electrodes 13 face the upper space 11. The air inlet holes 5 are perpendicular to the central axis 10 of the precombustor and are arranged at the axial middle position of the lower space 12, the air inlet holes 5 are connected in the circumferential tangential direction of the inner wall 14 of the lower space 12 when seen from the top view 3, and the air inlet holes 5 can enable the main combustion chamber 7 to communicate with the precombustor 1.
The lower end surface of the lower space 12 is provided with a jet valve 3 with pressure difference control, the jet hole 6 is arranged near the periphery of the jet valve 3, and the jet hole 6 can introduce the gas in the precombustion chamber 1 into the main combustion chamber 7 after the jet valve 3 is opened.
As shown in fig. 3 and 4, the prechamber 1 is a passive prechamber, and in the compression stroke, when the piston 15 is up, the gas pressure in the cylinder 7 (hereinafter referred to as "cylinder pressure") is higher than the gas pressure in the prechamber 1 (hereinafter referred to as "prechamber pressure"), and the jet valve 3 is closed by the pressure difference, and gas cannot enter the prechamber 1 from the jet valve 3. At the same time, the piston 15 presses the main mixture gas in the cylinder along the air inlet 5 and flows into the lower space 12 of the precombustor, and the air flow is sprayed at a high speed along the circumferential tangential direction of the inner wall 14 of the lower space 12, so that a spiral vortex 16 is formed in the lower space 12.
Referring to fig. 4, the front of the spiral vortex 16 rotates upwards and decelerates gradually along the spiral angle from the circumference of the inner wall 9 gradually expanding from the lower space 12 to the upper space 11 until reaching the electrode end face 17 of the spark plug, then the front of the spiral vortex 16 reversely flows into the socket 18 and is converted into an axial airflow 19 from top to bottom, the spark position between the positive electrode 13 and the negative electrode 13 of the spark plug is set at the socket 18, namely, the intersection point of the plane B-B and the central axis 10, the axial airflow 19 flowing downwards is smaller along the circumference diameter of the inner wall 9, the flowing speed is faster and faster, and the axial airflow 19 continuously adds into the spiral vortex 16 at the periphery of the inner wall 9 along the way reaching the lower space 12, so as to form an airflow motion model, namely, a spiral vortex model, which is closed and repeatedly flows downwards from the axial flow of the socket 18 near the central axis 10 of the pre-combustion chamber.
Fig. 5 is a B-B section of fig. 4, in which the gas flow velocity distribution is such that the gas flow velocity 20 near the outer circumference is higher than the gas flow velocity 21 near the inner circumference, and the gas flow velocity distribution in the C-C section and the A-A section is similar to the flow distribution in the B-B section.
In the pilot mixture of the spiral vortex model of the precombustion chamber, all gas components including carbon dioxide, oxygen and nitrogen and fuel are uniformly distributed, and the total non-uniformity of the gas concentration distribution is not more than 5%, so that the gas mixture can be regarded as a homogeneous mixture.
As shown in fig. 6, the spiral vortex model has several spaces with different air flow speeds and flow directions, each space has very remarkable characteristics, wherein:
the first, core region has the lowest air flow rate, below about 15 m/s, and is well suited for positioning spark plug electrodes, and is an ideal core generation region F. The space size of the fire core generation area F is a sphere with the diameter of about 2 to 4 mm taking the spark point of the spark plug electrode as the center;
second, under the shackles, the gas is accelerated axially and flows downwards, the flame front of the fire core is guided to a larger area rapidly, in the area, the gas flow speed is accelerated from 15 m/s close to the fire core generation area to more than 100 m/s close to the lower space from slow speed to fast speed, the fire core is ensured not to be blown out by the gas flow, and meanwhile, the fire core is promoted to grow rapidly, so that the gas flow type fire core growth area G is an ideal fire core growth area G. The fire core growing area G is an inverted cone with a base diameter of 4-6 mm and a height of 8-12 mm, and the axis of the inverted cone is overlapped with the axis 10 of the precombustion chamber;
third, the region further expanding in the radial and axial directions of the flame growth zone G up to the inner wall of the prechamber 1 is defined as flame development zone D. In this region, as the diameter Φ of the inner wall of the upper space 11 decreases, the downward velocity of the flame front increases further, and more air entrains the flame front into the high-velocity swirl of the peripheral spiral rise, which is at a velocity of up to 200 m/s to 1000 m/s, resulting in the flame front rapidly occupying the entire prechamber 1 space.
The precombustor volume is 0.1% to 0.5% of the cylinder single cylinder volume. In general, the larger the volume of the prechamber 1, the more the mass of the mixture entering the prechamber 1, and the more the mass of the fuel in the mixture, the more the heat generated by combustion increases, so that the temperature of the inner wall of the prechamber 1 increases, and the adverse effect of the pre-combustion is easily induced. Therefore, the volume of the prechamber 1 should be minimized if possible.
Further, the total flow area of the intake holes 5 is equal in value to 0.5% to 2% of the cylinder diameter. The spark plug 2 has a prechamber pressure of about 25% to 50% of the main combustion chamber pressure when it ignites. Similarly, the greater the pressure in the prechamber 1, the greater the mass of the mixture entering the prechamber 1, and the greater the mass of the fuel in the mixture, the greater the heat generated by combustion, so that the temperature of the inner wall of the prechamber 1 increases, and the adverse consequences of the preignition are easily induced. Therefore, if possible, the pressure in the prechamber 1 should be minimized, but not too low, at least the gas pressure after combustion of the pilot mixture should exceed the main combustion chamber gas pressure by 10%, preferably by 20%.
The total flow area of the jet holes 6 is 3.5 to 6 times the total flow area of the air intake holes 5. This ensures that more high-temperature high-pressure gas jets are injected into the main combustion chamber 4 in less crank angle time, and that higher main gas mixture ignition energy is achieved under lean conditions.
As shown in fig. 7, after the jet valve 3 is pushed open by the high-temperature and high-pressure gas, the high-temperature and high-pressure gas is injected from the precombustion chamber 1 into the main combustion chamber 4 in the direction of an arrow in the figure, so as to form an injection torch 22.
The pressure of the precombustion chamber in the prior art is generally equal to the pressure of the main combustion chamber, when the spark plug ignites the pilot mixed gas, the pilot mixed gas is ignited to raise the pressure, the precombustion chamber mixed gas immediately flows into the main combustion chamber due to the existence of pressure difference, at the moment, the temperature and the pressure of the gas flowing into the main combustion chamber are not high, the ignition effect on the main mixed gas is not achieved, the final pressure and the final temperature of the precombustion chamber mixed gas after combustion are reduced, the speed and the temperature of final gas jet flow are reduced, the formed jet flow torch is short and the temperature is insufficient, and the ignition on the main mixed gas is unfavorable. To achieve the effect of igniting the main mixture, it is necessary to increase the volume of the prechamber, increase the fuel entering the prechamber, and eventually increase the temperature and jet velocity of the jet gas, which is clearly a disadvantageous result.
The pressure of the pre-combustion chamber is obviously lower than the pressure of the main combustion chamber before ignition, the pressure of the pre-combustion chamber is lower than the pressure of the main combustion chamber within a period of time when the pilot mixed gas is ignited and combusted, the pilot mixed gas cannot flow into the main combustion chamber 4, the main mixed gas continuously flows into the pre-combustion chamber 1, and the pressure of the pre-combustion chamber is further increased under the combined action of the combustion of the pilot mixed gas and the continuously flowing mixed gas, so that the combustion speed of the pilot mixed gas is accelerated, and the combusted high-temperature pilot mixed gas cannot flow into the main combustion chamber 4 because the pressure does not exceed the pressure of the main combustion chamber. The combustion of the mixed gas is usually carried out at a low combustion heat release speed at the beginning, after a period of combustion, the combustion speed is rapidly increased, the pressure and the temperature of the precombustion chamber are accelerated and increased, the precombustion chamber exceeds the pressure of the main combustion chamber at a moment (within 1-2 crank angles), then the jet valve 3 is forced to be opened under the action of pressure difference because the pressure of the precombustion chamber is higher than the pressure of the main combustion chamber, a large jet flow area is formed, the pilot mixed gas is turned to be sprayed to the main combustion chamber 4 at a high speed in a high-temperature and high-pressure state, and more high-temperature and high-pressure gas jet flows in the precombustion chamber space enter the main combustion chamber in a few crank angles. This is one of the key steps to ensure that the lean mixture can be ignited and combustion is completed smoothly.
The lean mixture has two states. Firstly, the air-fuel ratio lambda of the mixture is equal to 1, and the EGR rate is 0% to 50%. The waste gas after the mixed gas in the state is combusted is very convenient to be treated by a three-way catalyst, and the cost is low. And secondly, the mixed gas is a mixed gas with an excessive air coefficient lambda far greater than 1, and because the mixed gas is in oxygen-enriched combustion, the excessive oxygen and nitrogen are combusted to form a nitrogen oxide NOx, and the tail gas treatment cost is high.
Alternatively, the prechamber wall is an integral part of the outer shell of the spark plug 2 or of an intermediate part connected between the spark plug 2 and the cylinder head 8.
Alternatively, a spark plug (not shown) is added to the cylinder 7 facing the main combustion chamber 4 for cold start and stable operation of the engine at low load.
Example 2
As shown in fig. 8, embodiment 2 of the present invention provides a helical vortex prechamber ignition system, wherein the inner wall of the upper space of the prechamber is shaped such that the generatrix of the rotating body thereof, which is gradually reduced in diameter, is an upwardly convex curve, and the rotation thereof generates an upwardly convex curved surface 23. The upward curved surface 23 causes the flow field of the air flow in the precombustion chamber 1 to be changed from that shown in fig. 4, so as to change the movement direction and speed of the air flow in the flame kernel generation area F, the flame kernel growth area G and the flame development area D. In general, the velocity of the swirling flow of the pilot mixture entering the prechamber will be reduced somewhat slower at the beginning than in example 1, the remainder being the same as in example 1.
Example 3
As shown in fig. 9, embodiment 3 of the present invention provides a helical vortex prechamber ignition system, wherein the inner wall of the upper space of the prechamber is shaped such that the generatrix of the rotating body thereof, which is gradually reduced in diameter, is a downward convex curve, and the rotation thereof generates a downward convex curve 24. The downward curved surface 24 causes the flow field of the air flow in the precombustion chamber 1 to be changed from that shown in fig. 4, so as to change the movement direction and speed of the air flow in the flame kernel generation area F, the flame kernel growth area G and the flame development area D. In general, the velocity of the swirling flow of the pilot mixture entering the prechamber will be reduced somewhat faster at the beginning than in example 1, the remainder being the same as in example 1.
Example 4
As shown in fig. 10, embodiment 4 of the present invention also provides a helical vortex prechamber ignition system, wherein the upper space 11 and the lower space 12 of the prechamber are integrated, and the inner wall is in the shape of an inverted cone 25 with gradually decreasing diameter. The reverse cone 25 causes the flow field of the air flow in the precombustion chamber 1 to be changed from that shown in fig. 4, and changes the movement direction and speed of the air flow in the flame kernel generation area F, the flame kernel growth area G and the flame development area D. In general, the lead mixture entering the prechamber will initially have a helix swirl angle that is greater than that of example 1, and thus the gas flow rises along axis 10 more rapidly, the remainder being the same as in example 1.
Example 5
As shown in fig. 11, embodiment 5 of the present invention further provides a spiral vortex prechamber ignition system, wherein the upper space 11 of the prechamber is a cylinder with larger diameter, the lower space is a cylinder with smaller diameter, and the two cylinders are connected by an inverted cone to form an inner wall curved surface 26 with a bus having an approximate U-shape. The curved surface 26 causes the flow field of the air flow in the precombustion chamber 1 to be changed from that shown in fig. 4, so that the movement direction and speed of the air flow in the flame kernel generation area F, the flame kernel growth area G and the flame development area D are changed. In general, the velocity of the swirling flow of the pilot mixture entering the prechamber will be reduced somewhat faster at the beginning than in example 3, the remainder being the same as in example 1.
The spiral vortex precombustor ignition system provided by the invention can be used for a single-cylinder or in-line multi-cylinder internal combustion engine, and can also be used for a V-type, W-type, opposite-type or rotor internal combustion engine.
The invention provides a spiral vortex precombustor ignition system, which can be used for fuels comprising gasoline, natural gas, a mixture of gasoline and ethanol, and/or other substance fuel compounds or mixtures.
The invention provides a spiral vortex precombustor ignition system, wherein the inner wall of the precombustor can have more shapes, no matter whether an air inlet 5 is vertical to a central axis 10, as long as intake air flow generates vortex air flow with a helix angle on the inner wall of a precombustor 1, and the air flow speed and the air flow direction of different spaces such as a fire core generation area F, a fire core growth area G, a flame development area D and the like formed in a spiral vortex model accord with the characteristics of the spiral vortex model, and the invention belongs to the protection scope of the invention.
In this specification, the reference to the main combustion chamber mixture and the main mixture refer to the mixture in the main combustion chamber, the prechamber mixture and the pilot mixture refer to the mixture in the prechamber, and the main combustion chamber is not limited to the position where the piston 15 reaches the top dead center, and the main combustion chamber mixture pressure, the cylinder pressure, the main combustion chamber gas pressure, and the main combustion chamber pressure refer to the main combustion chamber gas pressure, and the prechamber mixture pressure, the prechamber pilot mixture pressure, the prechamber gas pressure, and the prechamber pressure refer to the prechamber gas pressure.
Claims (15)
1. A helical swirl prechamber ignition system comprising a prechamber (1), a spark plug (2), a jet valve (3), a main combustion chamber (4), at least one inlet orifice (5) and at least one jet orifice (6); the precombustion chamber (1) is arranged in a cylinder cover (8) above the main combustion chamber (4) near the center of the cylinder (7); the main combustion chamber (4) is composed of a cylinder (7), a lower bottom surface of a cylinder cover (8) and a top surface of a piston (15); the prechamber (1) has an upper space (11) and a lower space (12); the method is characterized in that:
the shape of the inner wall (9) of the upper space and the shape of the inner wall (14) of the lower space are rotating bodies formed by rotating along the central axis (10) of the precombustion chamber, the diameter phi of the inner wall of the upper space (11) is gradually reduced from top to bottom and is connected with the diameter phi of the inner wall of the lower space (12), the diameter phi of the inner wall of the lower space (12) is a fixed value or gradually reduced from top to bottom, the positive and negative electrodes (13) of the spark plug are exposed to the upper space (11), the air inlet holes (5) are arranged at the axial middle position of the lower space (12), the air inlet holes (5) are connected in the circumferential tangential direction of the inner wall (14) of the lower space (12), and the air inlet holes (5) can enable gas communication between the main combustion chamber (4) and the precombustion chamber (1); the lower end face of the lower space (12) is provided with a jet valve (3) controlled by pressure difference, the jet hole (6) is arranged near the periphery of the jet valve (3), and the jet hole (6) can introduce the gas in the precombustion chamber (1) into the main combustion chamber (4) after the jet valve (3) is opened;
the pre-combustion chamber (1) is a passive pre-combustion chamber, in the compression stroke, when the piston (15) is in an upward direction, the gas pressure in the cylinder (7) is higher than the gas pressure in the pre-combustion chamber (1), the jet valve (3) is closed under the action of pressure difference, meanwhile, the piston (15) presses the main mixed gas in the cylinder (7) to flow into the lower space (12) of the pre-combustion chamber along the air inlet hole (5), and the air flow is sprayed at a high speed along the circumferential tangential direction of the inner wall (14) of the lower space (12), so that a spiral vortex (16) is formed in the lower space (12);
the front of the spiral vortex (16) rotates upwards and decelerates gradually along the spiral angle from the circumference of the inner wall (9) which is gradually enlarged from the lower space (12) to the upper space (11) until reaching the electrode end face (17) of the spark plug, then the front of the spiral vortex (16) reversely flows into the socket center (18) and is converted into an axial airflow (19) from top to bottom, a spark jump position between the positive electrode and the negative electrode (13) of the spark plug is arranged at the socket center (18), the axial airflow (19) flowing downwards is reduced along the circumference diameter of the inner wall (14) and the flow speed is accelerated, and on the way reaching the lower space (12), the axial airflow (19) is continuously added into the spiral vortex (16) at the periphery of the inner wall (14) of the pre-combustion chamber, and a closed and round airflow movement model, namely a spiral vortex model, is formed when the airflow is axially flows from the socket center (18) near the central axis (10) of the pre-combustion chamber.
2. The helical swirl prechamber ignition system of claim 1, characterized in that: in the pilot mixture of the spiral vortex model, all the gas components including carbon dioxide, oxygen and nitrogen, and fuel are uniformly distributed and form a homogeneous mixture.
3. The helical swirl prechamber ignition system of claim 1, characterized in that: in the spiral vortex model, the air flow speed distribution and the air flow movement direction distribution of the pilot mixed gas are stable and are not changed due to the change of the rotating speed of the internal combustion engine.
4. A helical swirl prechamber ignition system as in claim 1, characterized in that: the pre-combustion chamber is provided with a fire core generation area F, the fire core generation area F is a sphere, the sphere is positioned at a socket (18) of the spiral vortex model, the air flow speed of the area of the socket (18) is the lowest air flow speed area in the pre-combustion chamber, the air flow speed is not more than 15 m/s, the spark plug (2) is ensured to successfully ignite lean pilot gas mixture, and the fire core is successfully formed, but is not blown out by the air flow.
5. The helical swirl prechamber ignition system of claim 1, characterized in that: in the precombustion chamber, a flame growth zone G is arranged below a flame generation zone F, in the flame growth zone G, the air flow speed is changed from slow speed to fast speed, the air flow is accelerated downwards from 15 m/s close to the flame generation zone F to more than 80 m/s close to the lower space (12), the flame front of the flame is quickly guided to a larger area, the flame front of the flame is ensured not to be blown out by the air flow, and the flame front of the flame is simultaneously promoted to grow quickly.
6. A helical swirl prechamber ignition system as in claim 1, characterized in that: the precombustion chamber is provided with a flame development area D, and the flame development area D is formed by expanding the flame growth area G in the radial direction and the axial direction until the area of the inner wall of the precombustion chamber (1); in the flame development zone D, as the diameter phi of the inner wall of the upper space (11) is reduced, the downward speed of the flame front is further increased, more airflow is wrapped by the flame front and added into the high-speed vortex with the peripheral spiral rising, and at the moment, the airflow speed is up to 100 m/s to 1000 m/s, so that the flame front rapidly occupies the space of the whole precombustion chamber (1).
7. The helical swirl prechamber ignition system of claim 1, characterized in that: the total flow area of the intake holes (5) of the prechamber (1) is equal in value to 0.5% to 2% of the cylinder diameter; when the spark plug (2) ignites, the pressure of the precombustion chamber of the spark plug is 25 to 50 percent of the pressure of the main combustion chamber; the high pressure difference of the main combustion chamber (4) and the prechamber (1) results in a high velocity of the intake air flow, which is between 200 m/s and 1000 m/s.
8. The helical swirl prechamber ignition system of claim 1, characterized in that: the total flow area of the jet holes (6) is 3.5 to 6 times of the total flow area of the air inlet holes (5).
9. The helical swirl prechamber ignition system of claim 1, characterized in that: jet torch (22) formed by jetting the precombustion chamber (1) into the main combustion chamber (4) is uniformly distributed in the space of the main combustion chamber (4), so that the main mixed gas is ignited at multiple points at the same time, and the combustion duration of the main mixed gas is shortened.
10. The helical swirl prechamber ignition system of claim 1, characterized in that: the system is suitable for a mixture of the following two states: the first is that the mixture excess air ratio lambda is equal to (1), and the EGR rate is 0% to 50%; the second is or the mixture is a mixture with an excess air coefficient lambda far greater than 1.
11. The helical swirl prechamber ignition system of claim 1, characterized in that: the wall of the prechamber is a component of the cylinder head (8), or of the housing of the spark plug (2), or of an intermediate part connected between the spark plug (2) and the cylinder head (8).
12. The helical swirl prechamber ignition system of claim 1, characterized in that: the shape of the inner wall of the upper space of the precombustion chamber is that the generatrix of the rotating body is a convex curve, and the rotation of the generatrix generates a convex curved surface (23); or the shape of the inner wall of the upper space of the precombustion chamber is that the generatrix of the rotating body is a downward convex curve, and the rotation of the generatrix generates a downward convex curve (24); or the upper space (11) and the lower space (12) of the precombustion chamber are combined into a whole, and the shape of the inner wall of the precombustion chamber is an inverted cone (25) with gradually reduced diameter; or the upper space (11) of the precombustion chamber is a cylinder with larger diameter, the lower space is a cylinder with smaller diameter, and the two cylinders are connected by an inverted cone to form an inner wall curved surface (26) with a generatrix similar to a U shape.
13. The helical swirl prechamber ignition system of claim 1, characterized in that: a spark plug facing the main combustion chamber (4) is added in the cylinder (7) for cold start and stable operation of the internal combustion engine at low load.
14. The helical swirl prechamber ignition system of claim 1, characterized in that: it can be used for single cylinder or in-line multi-cylinder internal combustion engines, and also can be used for V-type, W-type, opposite type or rotor internal combustion engines.
15. The helical swirl prechamber ignition system of claim 1, characterized in that: the fuel used can be gasoline, natural gas, a mixture of gasoline and ethanol, and/or other substance fuel compounds or mixtures.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202111142276.XA CN113882938B (en) | 2021-09-28 | 2021-09-28 | Spiral vortex precombustion chamber ignition system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202111142276.XA CN113882938B (en) | 2021-09-28 | 2021-09-28 | Spiral vortex precombustion chamber ignition system |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN113882938A CN113882938A (en) | 2022-01-04 |
| CN113882938B true CN113882938B (en) | 2023-11-24 |
Family
ID=79007373
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202111142276.XA Active CN113882938B (en) | 2021-09-28 | 2021-09-28 | Spiral vortex precombustion chamber ignition system |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN113882938B (en) |
Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112814778B (en) * | 2020-12-31 | 2023-02-28 | 天津大学 | Air-assisted jet flame ignition device and ignition method thereof |
| CN114738160A (en) * | 2022-04-24 | 2022-07-12 | 哈尔滨东安汽车发动机制造有限公司 | A fire-breathing ignition system for a new energy vehicle engine |
| CN115013142A (en) * | 2022-04-28 | 2022-09-06 | 一汽解放汽车有限公司 | Engine combustion system |
| CN115013197B (en) * | 2022-06-19 | 2023-08-18 | 天津大学 | A Jet Mixer with Integrated Structure |
| US12078095B1 (en) | 2023-06-16 | 2024-09-03 | Saudi Arabian Oil Company | Internal pre-chamber (IPC) ignition device for turbulent jet ignition in reciprocating engines |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN206221056U (en) * | 2015-09-30 | 2017-06-06 | 卡特彼勒公司 | Internal combustion engine |
| JP2017137867A (en) * | 2016-02-06 | 2017-08-10 | プロメテウス アプライド テクノロジーズ，エルエルシー | Lean-burn pre-combustion chamber |
| CN108321678A (en) * | 2018-01-31 | 2018-07-24 | 山东大学 | A kind of precombustion-chamber ignition structure, system and its working method |
| CN112879145A (en) * | 2021-01-15 | 2021-06-01 | 湖南大兹动力科技有限公司 | Jet valve controlled precombustion chamber ignition internal combustion engine |
| CN113356994A (en) * | 2021-07-07 | 2021-09-07 | 湖南大兹动力科技有限公司 | Valve control jet ignition system |
-
2021
- 2021-09-28 CN CN202111142276.XA patent/CN113882938B/en active Active
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN206221056U (en) * | 2015-09-30 | 2017-06-06 | 卡特彼勒公司 | Internal combustion engine |
| JP2017137867A (en) * | 2016-02-06 | 2017-08-10 | プロメテウス アプライド テクノロジーズ，エルエルシー | Lean-burn pre-combustion chamber |
| CN108321678A (en) * | 2018-01-31 | 2018-07-24 | 山东大学 | A kind of precombustion-chamber ignition structure, system and its working method |
| CN112879145A (en) * | 2021-01-15 | 2021-06-01 | 湖南大兹动力科技有限公司 | Jet valve controlled precombustion chamber ignition internal combustion engine |
| CN113356994A (en) * | 2021-07-07 | 2021-09-07 | 湖南大兹动力科技有限公司 | Valve control jet ignition system |
Also Published As
| Publication number | Publication date |
|---|---|
| CN113882938A (en) | 2022-01-04 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN113882938B (en) | Spiral vortex precombustion chamber ignition system | |
| US6799551B2 (en) | Direct injection type internal combustion engine | |
| JP4100401B2 (en) | Internal combustion engine | |
| JP3073118B2 (en) | In-cylinder internal combustion engine | |
| US4193382A (en) | Stratified charge type combustion process for internal combustion engine and internal combustion engine utilizing same | |
| AU708365B2 (en) | Combined cycle engine | |
| US6318348B1 (en) | Stratified exhaust gas recirculation strategy for internal combustion engine | |
| JP2002188447A (en) | Internal combustion engine of direct in cylinder fuel injection | |
| US5224449A (en) | Lean-burn internal combustion system | |
| CN110905652A (en) | An engine with multiple high-pressure direct injection of natural gas in a cylinder and a stratified rapid combustion method thereof | |
| CN217898006U (en) | Combustion system and engine | |
| JP3747351B2 (en) | In-cylinder injection engine | |
| JP3873560B2 (en) | Combustion control device for internal combustion engine | |
| JP2003049650A (en) | Compressed self-ignition internal combustion engine | |
| US4088099A (en) | Mixture compressing, external auto-ignition four-stroke cycle internal combustion engine | |
| US4459804A (en) | Multiple spark ignition internal combustion engine with exhaust gas recirculation | |
| CN113756932A (en) | A pre-combustion chamber structure | |
| CN111997738B (en) | Compression ignition type internal combustion engine with spark control and control method thereof | |
| CN115045750A (en) | Combustion system and engine | |
| CN109578131B (en) | Oval combustion chamber | |
| JP3978965B2 (en) | Combustion control device for internal combustion engine | |
| CN217735605U (en) | Turbulent jet ignition device of long-channel precombustion chamber | |
| CN218760118U (en) | Gas supply system for promoting in-cylinder combustion based on jet swirl flame of pre-combustion chamber | |
| JP2007162631A (en) | Control device for internal combustion engine | |
| WO2006079818A1 (en) | Internal combustion engine |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| TA01 | Transfer of patent application right |
Effective date of registration: 20230626 Address after: No. 61, Weishan Road, Fushan District, Yantai City, Shandong Province 265500 Applicant after: Yantai Anxin Fine Blanking Technology Co.,Ltd. Address before: 410082 east area of incubation building of Hunan University Science and Technology Park, 186 Guyuan Road, Yuelu District, Changsha City, Hunan Province Applicant before: HUNAN DAZI POWER TECHNOLOGY Co.,Ltd. |
|
| TA01 | Transfer of patent application right | ||
| TA01 | Transfer of patent application right |
Effective date of registration: 20231030 Address after: 438021 No. 19 Xingang North Road, Donghu Street, Huangzhou District, Huanggang City, Hubei Province Applicant after: Hubei Huashun Fineblanking Technology Co.,Ltd. Address before: No. 61, Weishan Road, Fushan District, Yantai City, Shandong Province 265500 Applicant before: Yantai Anxin Fine Blanking Technology Co.,Ltd. |
|
| TA01 | Transfer of patent application right | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant |