CN111894727A - Four-valve direct-injection diesel engine combustion chamber - Google Patents
Four-valve direct-injection diesel engine combustion chamber Download PDFInfo
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- CN111894727A CN111894727A CN202010605577.0A CN202010605577A CN111894727A CN 111894727 A CN111894727 A CN 111894727A CN 202010605577 A CN202010605577 A CN 202010605577A CN 111894727 A CN111894727 A CN 111894727A
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- combustion chamber
- arc
- diesel engine
- direct injection
- injection diesel
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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
- F02B23/0618—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 having in-cylinder means to influence the charge motion
- F02B23/0624—Swirl flow
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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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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/10—Internal combustion engine [ICE] based vehicles
- Y02T10/12—Improving ICE efficiencies
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- 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 discloses a four-valve direct injection diesel engine combustion chamber, the axial section of the combustion chamber is omega-shaped, comprising: the upper arc is a spherical surface of the combustion chamber in contact with the arc on the top surface of the piston; the necking is positioned below the upper arc, is in an annular arc-shaped convex shape, and is in smooth transition with the lower arc of the upper arc; the bottom arc is positioned at the bottom of the combustion chamber, and the bottom arc is in smooth transition with the lower arc of the necking; the central boss is positioned in the center of the combustion chamber, and the top surface of the central boss is a plane and is in a circular truncated cone shape; and the generatrix of the side surface of the central boss is a straight line segment which forms a certain included angle with the central line of the combustion chamber and is tangent with the bottom arc. The invention enhances the mixing between the fuel and the air, is beneficial to reducing the emission and the oil consumption, effectively prevents the fuel from being directly injected to the cylinder sleeve, and reduces the heat load of the cylinder sleeve and the risk of burning the engine oil.
Description
Technical Field
The invention belongs to the technical field of automobile engines, and particularly relates to a four-valve direct injection type diesel engine combustion chamber.
Background
Chinese patent "direct injection diesel engine", publication No. CN102892992A, publication No. 2013.01.23, provides a four-valve direct injection diesel engine and a piston for use in such an engine in which the fuel-air mixture is mixed more intensively and thoroughly than before, resulting in a reduction in emissions and an increase in engine efficiency. The direct injection diesel engine combustion chamber disclosed in this patent does not meet the diesel engine combustion requirements at high compression ratios. In order to improve the fuel economy of diesel engines, it is one of the technical measures to increase the compression ratio, and the volume of the combustion chamber needs to be reduced. The included angle of the conical or truncated conical protrusion of the combustion chamber is 104-108 degrees, the reduction of the volume of the combustion chamber can only reduce the diameter of the outlet of the combustion chamber, so that fuel steam collides with the wall surface of the necking in advance, the quality of mixed gas in the pit is deteriorated, and the fuel economy is deteriorated.
Chinese patent "combustion chamber of direct injection diesel engine", publication No. CN109404156A, publication No. 2019.03.01, provides a combustion chamber of direct injection diesel engine, which is located at the center or non-center of the piston top surface of the piston body, and above the pin hole, the radial direction of the combustion chamber is circular, the axial cross-section is omega-shaped, the combustion chamber includes upper step, throat, bottom arc and central boss. The patent comprises an upper step, a necking, a bottom arc and a central boss. The central boss is of a structure formed by stacking three circular truncated cones, and the design structure is complex. The upper step and the necking are easy to cause fuel oil bundles to be sprayed out of the combustion chamber and flow limited to the cylinder wall, so that incomplete combustion is caused, and the necking is easy to crack.
The Chinese patent 'a cylinder piston of a diesel engine and a combustion chamber applying the same', publication No. CN103696870B, publication No. 2016.03.16, discloses a cylinder piston of a diesel engine, the top surface of which is provided with a combustion chamber with an axial section outline in omega shape, the outer side inner wall of the combustion chamber is provided with an arc ridge extending inwards to a cavity, and the combustion chamber is divided into an inner side conventional area and a groove area by a tangent line formed by the radial protruded highest point of the arc ridge; the outer edge of the throat opening of the combustion chamber is provided with a groove to form a buffer zone communicated with the groove zone, and the outer contour of the buffer zone changes in a gradually approaching trend from the groove zone to the top surface of the piston. The trend of the upper vortex can be adjusted, and the problem of high thermal load on the bottom surface of the cylinder cover can be effectively avoided on the basis of meeting the requirements of improving the thermal efficiency and reducing the oil consumption. However, there are the following problems: the throat of the combustion chamber consists of a straight line section 4, a straight line section 6 and an arc connecting the straight line section 4 and the straight line section 6 and having a radius of 4-5mm, wherein an included angle between the straight line section 4 and a horizontal plane is 8-10 degrees, an included angle between the straight line section 6 and the horizontal plane is 65-75 degrees, and the ratio of the distance L from the radially protruded highest point of an arc ridge to the center line of a piston to the maximum diameter L of a conventional area A of the combustion chamber is 0.7-0.75. Particularly, most of the existing diesel engines adopt a combustion system with high compression ratio and high oil injection pressure, the explosion pressure of the combustion system is high, the combustion temperature is high, and the problems of oxidation stripping of a throat of a piston or cracking of the throat and the like caused by overhigh thermal load of the throat are easily caused, so that the reliability of the piston is influenced.
With the upgrading of emission regulations, the market of commercial vehicles is more and more competitive, and higher requirements are put on the economy and the emission performance of diesel engines. The thermal efficiency of the diesel engine is improved by improving the compression ratio, and the structure of the combustion chamber needs to be optimally adjusted.
Disclosure of Invention
In view of the problems in the prior art, the invention aims to provide a four-valve direct injection diesel engine combustion chamber which can effectively improve the thermal efficiency of a diesel engine and reduce the emission.
In order to achieve the above object, a four-valve direct injection diesel engine combustion chamber according to the present invention is characterized by having an omega-shaped axial cross-section, and comprising:
the upper arc is a spherical surface of the combustion chamber in contact with the arc on the top surface of the piston;
the necking is positioned below the upper arc, is in an annular arc-shaped convex shape, and is in smooth transition with the lower arc of the upper arc;
the bottom arc is positioned at the bottom of the combustion chamber, and the bottom arc is in smooth transition with the lower arc of the necking;
the central boss is positioned in the center of the combustion chamber, and the top surface of the central boss is a plane and is in a circular truncated cone shape; and the generatrix of the side surface of the central boss is a straight line segment which forms a certain included angle with the central line of the combustion chamber and is tangent with the bottom arc.
Preferably, the ratio of the distance V2 from the center of the circular arc of the necking to the top surface of the piston to the depth V1 of the combustion chamber is between 0.51 and 0.56. Therefore, the circular arc of the necking is positioned at the middle section of the combustion chamber, and the mixed gas which flows to the upper part of the combustion chamber in an eddy mode also has enough space for rapid mixing.
Preferably, the ratio of the minimum distance V3 between the central boss and the top surface of the piston to the depth V1 of the combustion chamber is between 0.21 and 0.23.
Preferably, the ratio of the minimum diameter B of the necking to the maximum inner diameter C of the combustion chamber in the lower region of the throat is 0.99-1.
Preferably, the ratio of the minimum diameter B of the necking to the diameter of the top surface of the piston of the cylinder is 0.58-0.59.
Preferably, the radius of the necking arc is 2-2.1 mm.
Preferably, the ratio of the maximum opening diameter A to the diameter of the top surface of the piston of the cylinder is 0.73-0.74.
Preferably, the radius of the upper arc is 18-18.1 mm.
Preferably, the radius of the bottom arc is 7.5-7.6 mm.
Preferably, the generatrix of the side surface of the central boss is smoothly transited with the top surface of the central boss through a boss arc.
Preferably, the included angle between the lateral generatrices of the central lug boss is alpha, and alpha is more than or equal to 115 degrees and less than or equal to 135 degrees.
The invention has the beneficial effects that: the invention uses the arc ridge to cause the flow separation of fuel oil jet flow, disturbs the vortex in the cylinder and forms double vortices so as to promote mixing and improve combustion. When the combustion system is matched with a combustion system with high rail pressure (about 2000 bar), high compression ratio (20-21), proper air intake swirl ratio and proper oil injection included angle, particle emission and effective fuel consumption rate can be greatly reduced. The fuel injected into the necking arc forms two paths of airflow movement, and the upward mixed fuel is sucked to the areas of the top surface of the piston and the bottom surface of the cylinder cover, so that the fresh air is fully utilized, and the space distribution of the fuel in the cylinder is more uniform; the downward mixed gas is along the bottom arc, the side bus of the central boss, and the boss arc and the central boss are sucked to the center of the combustion chamber, so that fuel oil and flame can be expanded to the center of the combustion chamber, and the heat loss at the wall surface of the piston is reduced.
The combustion chamber structure of the invention enables more unburned fuel to expand towards the middle of the combustion chamber with more sufficient air, enhances the mixing between the fuel and the air and is beneficial to reducing the emission and the oil consumption. More fuel can enter a conventional area of a combustion chamber by adjusting the position of the fuel colliding with the wall, the fuel can be effectively prevented from being directly sprayed to the cylinder sleeve, and the heat load of the cylinder sleeve and the risk of burning the engine oil are reduced.
Simulation results show that under the partial load working condition, the indicated thermal efficiency of the combustion chamber can be improved by 2.7 percent to the maximum extent, and the indicated specific oil consumption can be improved by 5 g/kw.h to the maximum extent.
Drawings
FIG. 1 is a schematic axial cross-sectional view of a combustor of the present invention
FIG. 2 is a schematic representation of the movement of injected fuel into the combustion chamber of the present invention
In the figure: 1. the piston comprises a piston body, 2, a piston top surface, 3, an upper arc, 4, a necking, 5, a bottom arc, 6, a central boss side bus, 7, a boss arc, 8, a central boss, 9, a combustion chamber central line, 10, an upper space, 11 and a lower space; alpha, the included angle between the side surface generatrix lines of the central boss, A, the maximum opening diameter, B, the minimum diameter of the reducing port, C, the maximum diameter of the lower space of the combustion chamber, V1, the depth of the combustion chamber, V2, the distance between the circle center of the reducing port circular arc and the top surface of the piston, and V3, the minimum distance between the central boss and the top surface of the piston.
Detailed Description
The technical solutions of the present invention (including the preferred ones) are further described in detail by way of fig. 1 to 2 and enumerating some alternative embodiments of the present invention. It is to be understood that the described embodiments are merely a few embodiments of the invention, and not all embodiments. All other embodiments, which can be derived by a person skilled in the art from the embodiments of the present invention without any inventive step, are within the scope of the present invention.
As shown in figures 1 and 2, the four-valve direct injection diesel engine combustion chamber designed by the invention is positioned at the center or non-center of the top surface 2 of the piston body 1, the axial section of the combustion chamber is omega-shaped, and the combustion chamber comprises an upper circular arc 3, a necking 4, a bottom circular arc 5 and a central boss 8. The region above the constriction 4 forms an upper space 10 and the region below the constriction 4 forms a lower space 11.
An upper arc 3, which is a spherical surface where the combustion chamber contacts with the top surface 2 of the piston;
the necking 4 is positioned below the upper arc 3, the necking 4 is in an annular arc-shaped convex shape and is in smooth transition with the lower arc of the upper arc 3;
the bottom arc 5 is positioned at the bottom of the combustion chamber, and the bottom arc 5 is in smooth transition with the lower arc of the necking 4;
the central boss 8 is positioned in the center of the combustion chamber, and the top surface of the central boss 8 is a plane and is in a circular truncated cone shape; and the side surface generatrix 6 of the central boss is a straight line segment which forms a certain included angle with the central line 9 of the combustion chamber and is tangent with the bottom circular arc 5. Preferably, the top surfaces of the central boss side generatrix 6 and the central boss 8 are in smooth transition through a boss arc 7. The included angle between the lateral generatrix 6 of the central lug boss is alpha, and the alpha is more than or equal to 115 degrees and less than or equal to 135 degrees.
Preferably, the ratio of the distance V2 from the center of the circular arc of the necking to the top surface of the piston to the depth V1 of the combustion chamber is between 0.51 and 0.56. Thus, by adjusting the ratio of V1 to V2, the arc of the necking is positioned at the middle section of the combustion chamber, so that the mixed gas which flows to the upper part of the combustion chamber in a swirling mode has enough space for rapid mixing.
Preferably, the ratio of the minimum distance V3 between the central boss and the top surface of the piston to the depth V1 of the combustion chamber is between 0.21 and 0.23.
Preferably, the ratio of the minimum diameter B of the throat (also called as small diameter of the combustion chamber) to the maximum inner diameter C of the combustion chamber in the lower area of the throat (also called as large diameter of the combustion chamber) is 0.99-1, and the radius of the arc of the throat is 2-2.1 mm, so that the arc ridge of the throat does not protrude towards the inside of the combustion chamber too much, and the distance between the arc ridge of the throat and the cooling oil passage of the piston is short. The radius of the upper arc 3 connected with the necking 4 is 18-18.1 mm, the radius of the bottom arc is 7.5-7.6 mm, the contact surface between the combustion chamber and the piston cooling oil channel is large, and the risk of throat failure caused by too fast rise of thermal load can be reduced.
Preferably, the ratio of the minimum diameter B of the necking to the diameter of the top surface of the piston of the cylinder is 0.58-0.59.
Preferably, the ratio of the maximum opening diameter A to the diameter of the top surface of the piston of the cylinder is 0.73-0.74.
The combustion chamber of the invention is characterized in that two arcs are designed to be connected by a necking arc, and the combustion chamber is divided into an upper part and a lower part. For the upper part of the combustion chamber, the position, the arc radius and the diameter of the opening at the upper part of the combustion chamber are determined by the circle center position of the necking arc with reasonable design and two values of V2 and B, so that the proportion of fuel steam sprayed into the upper part of the combustion chamber is reasonable. Through adjusting the included angle alpha between the side buses of the lug boss, the mixed gas is obviously enhanced to be mixed with the air on the upper part of the central lug boss under the drainage effect of the bottom circular arc, the quantity of unburned hydrocarbons is reduced to the maximum degree, and the generation of carbon smoke particles is reduced to the same maximum degree.
It will be understood by those skilled in the art that the foregoing is only a preferred embodiment of the present invention, and is not intended to limit the invention, and any modification, combination, replacement, or improvement made within the spirit and principle of the present invention is included in the scope of the present invention.
Claims (10)
1. A four-valve direct injection diesel engine combustion chamber having an omega-shaped axial cross-section, comprising: the upper arc is a spherical surface of the combustion chamber in contact with the arc on the top surface of the piston; the necking is positioned below the upper arc, is in an annular arc-shaped convex shape, and is in smooth transition with the lower arc of the upper arc; the bottom arc is positioned at the bottom of the combustion chamber, and the bottom arc is in smooth transition with the lower arc of the necking; the central boss is positioned in the center of the combustion chamber, and the top surface of the central boss is a plane and is in a circular truncated cone shape; and the generatrix of the side surface of the central boss is a straight line segment which forms a certain included angle with the central line of the combustion chamber and is tangent with the bottom arc.
2. The four-valve direct injection diesel engine combustion chamber of claim 1, characterized in that: the ratio of the distance V2 between the center of the circular arc of the necking and the top surface of the piston to the depth V1 of the combustion chamber is between 0.51 and 0.56.
3. The four-valve direct injection diesel engine combustion chamber of claim 1, characterized in that: the ratio of the minimum distance V3 between the central boss and the top surface of the piston to the depth V1 of the combustion chamber is 0.21-0.23; the ratio of the minimum diameter B of the necking to the maximum inner diameter C of the combustion chamber in the lower area of the throat is 0.99-1.
4. The four-valve direct injection diesel engine combustion chamber according to claim 1 or 2, characterized in that: the ratio of the minimum diameter B of the necking to the diameter of the top surface of the piston of the cylinder is 0.58-0.59.
5. The four-valve direct injection diesel engine combustion chamber of claim 4, characterized in that: the radius of the necking arc is 2-2.1 mm.
6. The four-valve direct injection diesel engine combustion chamber of claim 1, characterized in that: the ratio of the maximum opening diameter A to the diameter of the top surface of the piston of the cylinder is 0.73-0.74.
7. The four-valve direct injection diesel engine combustion chamber of claim 1, characterized in that: the radius of the upper arc is 18-18.1 mm.
8. The four-valve direct injection diesel engine combustion chamber of claim 1, characterized in that: the radius of the bottom arc is 7.5-7.6 mm.
9. The four-valve direct injection diesel engine combustion chamber of claim 1, characterized in that: and the bus on the side surface of the central boss is in smooth transition with the top surface of the central boss through a boss arc.
10. The four-valve direct injection diesel engine combustion chamber according to claim 1 or 9, characterized in that: the included angle between the lateral generatrices of the central lug boss is alpha, and the alpha is more than or equal to 115 degrees and less than or equal to 135 degrees.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202010605577.0A CN111894727A (en) | 2020-06-29 | 2020-06-29 | Four-valve direct-injection diesel engine combustion chamber |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202010605577.0A CN111894727A (en) | 2020-06-29 | 2020-06-29 | Four-valve direct-injection diesel engine combustion chamber |
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| CN111894727A true CN111894727A (en) | 2020-11-06 |
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| CN202010605577.0A Pending CN111894727A (en) | 2020-06-29 | 2020-06-29 | Four-valve direct-injection diesel engine combustion chamber |
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Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114109584A (en) * | 2021-12-08 | 2022-03-01 | 天津大学 | Spark plug assisted high octane fuel compression ignition open type combustion chamber |
| CN114320641A (en) * | 2022-03-11 | 2022-04-12 | 潍柴动力股份有限公司 | Engine combustion system, control method and engine |
| CN115680928A (en) * | 2022-11-18 | 2023-02-03 | 中国重汽集团济南动力有限公司 | Piston, diesel engine and vehicle |
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| EP1251252A1 (en) * | 2000-01-25 | 2002-10-23 | Kabushiki Kaisha Toyota Chuo Kenkyusho | Direct injection type internal combustion engine |
| EP1316710A1 (en) * | 2001-11-30 | 2003-06-04 | Renault s.a.s. | Piston for an internal combustion engine and engine provided therewith |
| CN1587660A (en) * | 2004-08-31 | 2005-03-02 | 侯德洋 | Combustion system and method for self adaption controllable heat premixing direct jet type diesel engine |
| CN103670775A (en) * | 2012-09-14 | 2014-03-26 | 斗山英维高株式会社 | Combustion Bowl Shape Of Direct Injection Diesel Engine For Reducing The Soot Emission |
| CN108412603A (en) * | 2018-04-25 | 2018-08-17 | 江苏四达动力机械集团有限公司 | Piston combustion chamber structure |
| CN109404156A (en) * | 2018-12-10 | 2019-03-01 | 广西玉柴机器股份有限公司 | The combustion chamber of diesel engine with direct injection |
-
2020
- 2020-06-29 CN CN202010605577.0A patent/CN111894727A/en active Pending
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP1251252A1 (en) * | 2000-01-25 | 2002-10-23 | Kabushiki Kaisha Toyota Chuo Kenkyusho | Direct injection type internal combustion engine |
| EP1316710A1 (en) * | 2001-11-30 | 2003-06-04 | Renault s.a.s. | Piston for an internal combustion engine and engine provided therewith |
| CN1587660A (en) * | 2004-08-31 | 2005-03-02 | 侯德洋 | Combustion system and method for self adaption controllable heat premixing direct jet type diesel engine |
| CN103670775A (en) * | 2012-09-14 | 2014-03-26 | 斗山英维高株式会社 | Combustion Bowl Shape Of Direct Injection Diesel Engine For Reducing The Soot Emission |
| CN108412603A (en) * | 2018-04-25 | 2018-08-17 | 江苏四达动力机械集团有限公司 | Piston combustion chamber structure |
| CN109404156A (en) * | 2018-12-10 | 2019-03-01 | 广西玉柴机器股份有限公司 | The combustion chamber of diesel engine with direct injection |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114109584A (en) * | 2021-12-08 | 2022-03-01 | 天津大学 | Spark plug assisted high octane fuel compression ignition open type combustion chamber |
| CN114320641A (en) * | 2022-03-11 | 2022-04-12 | 潍柴动力股份有限公司 | Engine combustion system, control method and engine |
| CN115680928A (en) * | 2022-11-18 | 2023-02-03 | 中国重汽集团济南动力有限公司 | Piston, diesel engine and vehicle |
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Application publication date: 20201106 |