CN109404156B - Combustion chamber of direct injection diesel engine - Google Patents
Combustion chamber of direct injection diesel engine Download PDFInfo
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- CN109404156B CN109404156B CN201811503333.0A CN201811503333A CN109404156B CN 109404156 B CN109404156 B CN 109404156B CN 201811503333 A CN201811503333 A CN 201811503333A CN 109404156 B CN109404156 B CN 109404156B
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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
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Abstract
The invention discloses a combustion chamber of a direct injection diesel engine, which is positioned at the center or non-center of the top surface of a piston body. The upper step is an annular surface of the combustion chamber contacted with the circular arc of the top surface of the piston, and the axial section of the upper step comprises a first step straight line section and a second step straight line section from top to bottom; the necking is positioned below the upper step, is in an annular arc-shaped convex shape and is connected with a smooth arc at the lower part of the straight line section of the second step; the bottom arc is positioned at the bottom of the combustion chamber and is connected with the lower smooth arc of the necking; the central boss is positioned in the center of the combustion chamber, is substantially in a circular truncated cone shape, and comprises a first boss, a second boss and a third boss which are piled up from top to bottom; the lower part of the third boss is connected with the bottom arc smooth arc. Therefore, the purpose of improving fuel economy and reducing pollutant emission can be achieved.
Description
Technical Field
The invention relates to the field of diesel engine manufacturing, in particular to a combustion chamber of a direct injection diesel engine.
Background
At present, national regulations aiming at the fuel economy of a diesel engine and the emission limit of tail gas pollutants are continuously improved, strict national Liua emission regulations are implemented on diesel engine powered urban vehicles in 7 months in 2020, the fuel consumption limit of heavy commercial vehicles in the third stage is implemented in 7 months in 2019, and the limit of the third stage is reduced by 15% compared with the limit of the second stage. Therefore, in order to meet the requirements of the regulations, an efficient and clean combustion system must be designed, wherein the shape of a combustion chamber is one of the keys of the combustion system of the diesel engine, and the in-cylinder oil-gas mixing process must be reasonably organized according to the characteristics of the operating conditions of the diesel engine, so that the aims of fully combusting and inhibiting the generation of pollutants are fulfilled.
The typical direct-injection diesel combustion chamber shape is now a necked omega shape, see fig. 1, and its modified shape, see fig. 2. The omega-shaped combustion chamber is located in the center or non-center of the piston top face 2 of the piston body 1. Fig. 1-2 illustrate embodiments located at the center.
The omega-shaped combustion chamber is characterized in that: a boss 3 is arranged in the center of the combustion chamber, the boss is mostly in a circular truncated cone shape, the top of part of the boss of the combustion chamber is a spherical surface, and the side surface 9 of the boss extends towards the bottom of the combustion chamber; the combustion chamber reaches its maximum diameter, forming a lower combustion chamber space 15, which then, as it extends again towards the piston crown, gradually decreases in diameter to a minimum value, so that the combustion chamber forms a constriction 11, also called throat, which then remains constant or is slightly enlarged by a chamfer radius before reaching the piston crown 2.
The necking omega-shaped deformation combustion chamber is characterized in that: when extending from the throat 11 to the piston crown 2, the combustion chamber diameter increases again, and an upper combustion chamber space 14 is formed between the throat 11 and the piston crown 2 in a stepped or inclined shape. The omega-shaped combustion chamber with the reduced opening is matched with the air inlet vortex, so that air in the combustion chamber can be fully utilized for tissue combustion; and the deformed omega-shaped combustion chamber with step or slope transition enlarges the upper combustion chamber space 14, improves the oil-gas mixing quality in the cylinder, improves the combustion economy and reduces the soot emission.
The top surface of a typical omega-shaped combustion chamber central boss is a plane or a spherical surface, and a generatrix of the side surface of the boss is a straight line which forms a certain included angle with the central line of the combustion chamber and is tangent with an arc at the bottom of the combustion chamber. The boss is used for extruding air in the center of the combustion chamber to two sides to promote oil-gas mixing in the stage of injecting fuel oil into the combustion chamber, and guiding mixed air entering the bottom of the combustion chamber to the center of the combustion chamber and continuing guiding in the descending stage of the piston. The included angle between the lateral generatrix of the boss and the central line of the combustion chamber is determined by the depth of the combustion chamber, the smaller the depth of the combustion chamber is, the larger the included angle between the lateral generatrix of the boss and the central line of the combustion chamber is, the more gentle the lateral surface of the boss is, and the more easily the mixed gas entering the pit moves towards the center.
In order to improve the fuel economy of diesel engines, it is one of the technical measures to increase the compression ratio, which means that the combustion chamber volume needs to be reduced. The combustion chamber volume may be reduced by reducing the combustion chamber depth or combustion chamber diameter alone or by reducing both the combustion chamber depth and combustion chamber diameter. After the combustion chamber degree of depth reduces, the side that makes the boss is closer apart from the nozzle opening axis, and the boss side also becomes gentle, and the gas mixture that gets into the combustion chamber bottom can converge with the gas mixture that orifice axis direction formed under the boss side water conservancy diversion and make the gas mixture rich excessively, causes the postcombustion phase heat release rate to reduce, and the duration of burning is lengthened, and fuel economy and soot emission worsen. The depth of the combustion chamber can be kept unchanged by reducing the diameter (including a large diameter and a small diameter) of the combustion chamber, but fuel steam is enabled to collide with the necking wall face too early, the movement development space of the mixed gas entering the bottom of the combustion chamber is reduced, the path reaching the slope of the boss is shortened, the quality of the mixed gas in the pit is deteriorated, the mixed gas reaches the side face of the boss at an earlier moment and starts to climb to move towards the center of the combustion chamber, the heat release rate in the post-combustion period is reduced, the combustion is continuously increased, and the fuel economy and the soot emission are deteriorated. Meanwhile, the method for reducing the depth and the diameter of the combustion chamber cannot eliminate the quality deterioration of the mixed gas, and cannot achieve the purposes of improving the fuel economy and inhibiting the pollutant emission of the combustion chamber with high compression ratio.
The information disclosed in this background section is only for enhancement of understanding of the general background of the invention and should not be taken as an acknowledgement or any form of suggestion that this information forms the prior art already known to a person skilled in the art.
Disclosure of Invention
The object of the present invention is to provide a combustion chamber for a direct injection diesel engine which is well adapted to overcome the drawbacks of the combustion chambers of the prior art described above.
In order to achieve the above object, the present invention provides a combustion chamber of a direct injection diesel engine, which is located at the center or non-center of the top surface of a piston body and above a pin hole, wherein the combustion chamber has a radial shape and an axial cross-section of an omega shape, and comprises an upper step, a throat, a bottom arc and a central boss. The upper step is an annular surface of the combustion chamber contacted with the circular arc of the top surface of the piston, and the axial section of the upper step comprises a first step straight line section and a second step straight line section from top to bottom; the necking is positioned below the upper step, is in an annular arc-shaped convex shape and is connected with a smooth arc at the lower part of the straight line section of the second step; the bottom arc is positioned at the bottom of the combustion chamber and is connected with the lower smooth arc of the necking; the central boss is positioned in the center of the combustion chamber, is substantially in a circular truncated cone shape, and comprises a first boss, a second boss and a third boss which are piled up from top to bottom; the lower part of the third boss is connected with the bottom arc smooth arc.
In a preferred embodiment, the included angle between the first step straight-line segment and the top surface of the piston is 53-57 degrees, the included angle between the second step straight-line segment and the top surface of the piston is 18-22 degrees, and the first step straight-line segment is connected with the second step straight-line segment in a smooth circular arc mode.
In a preferred embodiment, the ratio of the distance from the center of the circular arc of the throat to the top face of the piston to the depth of the combustion chamber is between 0.35 and 0.45; the ratio of the maximum opening diameter of the top of the first step straight-line section to the minimum diameter of the necking is 1.30-1.32.
In a preferred embodiment, the axial cross-section of the central boss includes, from top to bottom, a first boss side generatrix, a second boss side platform generatrix and a third boss side generatrix.
In a preferred embodiment, the first boss side surface generatrix is smoothly transitionally connected with the top surface of the central boss through a boss circular arc; a bus on the side surface of the third boss is smoothly and transitionally connected with an arc at the bottom; the first boss side surface bus and the second boss side surface bus are in smooth transition connection through a first bus transition arc; and the second boss side surface platform bus and the third boss side surface bus are in smooth transition connection through a second bus transition arc.
In a preferred embodiment, the included angle between the first boss side generatrix and the central line of the combustion chamber is larger than the included angle between the second boss side generatrix and the central line of the combustion chamber, and the included angle between the first boss side generatrix and the central line of the combustion chamber is smaller than the included angle between the third boss side generatrix and the central line of the combustion chamber.
In a preferred embodiment, the ratio of the distance from the center line of the combustion chamber to the maximum diameter of the lower space of the combustion chamber at the intersection of the extension line of the first boss side surface generatrix and the extension line of the second boss side surface generatrix is 0.05 to 0.095.
In a preferred embodiment, the top surface of the central boss is lower than the top surface of the piston.
Compared with the prior art, the combustion chamber of the direct injection diesel engine has the following beneficial effects: the central boss of the combustion chamber is formed by piling three round tables, side surface buses of the three round tables are connected in a smooth transition mode through two sections of circular arcs between the side surface buses, the included angle between each section of side surface buses from top to bottom and the central line of the combustion chamber is larger than that between each section of side surface buses and that between each section of side surface buses. And then the reasonable design of the circle center position and the arc radius of the necking arc, the diameter of the opening at the upper part of the combustion chamber and the angle of two step straight-line segments forming a step surface ensures that the proportion of the fuel steam sprayed into the upper part of the combustion chamber is reasonable. The combustion chamber has high utilization rate on the air in the squeezing area, and can not enable a large amount of high-temperature gas to move to the wall surface of the cylinder; therefore, the quality of mixed gas in the post-combustion period can be improved, the heat release rate of combustion is improved, the oxidation of soot in a cylinder is promoted, the generation of a large amount of nitrogen oxide is inhibited, and the aims of improving the fuel economy and reducing the emission of pollutants are fulfilled.
Drawings
FIG. 1 is an axial cross-sectional schematic view of a combustor in accordance with one embodiment of the prior art.
FIG. 2 is an axial cross-sectional schematic view of another embodiment of a prior art combustor.
FIG. 3 is an axial cross-sectional schematic view of a combustor according to an embodiment of the present invention.
FIG. 4 is a schematic diagram of the injected fuel movement of a combustion chamber according to an embodiment of the present invention.
Description of the main reference numerals:
1-piston body, 2-piston top surface, 3-center boss, 4-boss arc, 5-first boss side bus, 6-first bus transition arc, 7-second boss side platform bus, 8-second bus transition arc, 9-third boss side bus, 10-bottom arc, 11-necking, 12-second step straight line segment, 13-first step straight line segment, 14-upper space, 15-lower space, 16-combustion chamber center line, α -included angle of first boss side bus and combustion chamber center line, β -included angle of second boss side platform bus and combustion chamber center line, gamma-included angle of third boss side bus and combustion chamber center line, α 1-included angle of first step straight line segment and piston top surface, α 2-included angle of second step straight line segment and piston top surface, D1-most with opening diameter, D2-necking minimum diameter (combustion chamber), D3-maximum diameter of combustion chamber lower space (combustion chamber large diameter), R-first boss side surface extension line and second boss side surface extension line, distance of combustion chamber center line, combustion chamber top surface distance H-combustion chamber center distance.
Detailed Description
The following detailed description of the present invention is provided in conjunction with the accompanying drawings, but it should be understood that the scope of the present invention is not limited to the specific embodiments.
Throughout the specification and claims, unless explicitly stated otherwise, the word "comprise", or variations such as "comprises" or "comprising", will be understood to imply the inclusion of a stated element or component but not the exclusion of any other element or component.
As shown in fig. 3 to 4, fig. 3 is an axial sectional view of a combustion chamber according to an embodiment of the present invention. FIG. 4 is a schematic diagram of the injected fuel movement of a combustion chamber according to an embodiment of the present invention. The combustion chamber of the direct injection diesel engine is positioned at the center or non-center of the top surface 2 of the piston body 1 and above the pin hole, the radial direction of the combustion chamber is circular, the axial section of the combustion chamber is similar to omega shape, the combustion chamber is actually omega shape and is formed by revolving along the center line 16 of the combustion chamber, and the combustion chamber comprises an upper step, a reducing 11, a bottom circular arc 10 and a central boss 3. The region above the throat 11 forms an upper space 14 and the region below the throat 11 forms a lower space 15.
In some embodiments, the upper step is an annular surface where the combustion chamber contacts the piston top surface 2 through an arc, and the axial section of the upper step comprises a first step straight line segment 13 and a second step straight line segment 12 from top to bottom. The included angle between the first step straight-line section 13 and the piston top surface 2 is 53-57 degrees, the included angle between the second step straight-line section 12 and the piston top surface 2 is 18-22 degrees, and the first step straight-line section 13 and the second step straight-line section 12 are connected in a smooth circular arc mode. The annular surface of the upper step of the combustion chamber is actually formed by the connection of a first step straight-line segment 13 and a second step straight-line segment 12 and a smooth circular arc along the rotation of the center line 16 of the combustion chamber.
In some embodiments, the throat 11 is located below the upper step, and the throat 11 is in the shape of an annular arc protrusion and is engaged with a lower smooth arc of the second step straight line segment 12. The position of the arc forming the throat 11 determines the throat diameter D2 (small diameter of the combustion chamber) and the distance H of the throat 11 relative to the piston top surface 2, and the ratio of the distance H of the center of the arc of the throat 11 from the piston top surface 2 to the depth H of the combustion chamber is 0.35-0.45; the ratio of the maximum opening diameter D1 of the top of the first step straight line section 13 to the minimum diameter D2 of the necking 11 is between 1.30 and 1.32.
In some embodiments, the bottom arc 10 is located at the bottom of the combustion chamber, and the bottom arc 10 is engaged with the lower smooth arc of the throat 11 at the top and with the lower smooth arc of the third boss of the central boss 3 at the bottom. The bottom arc 10 extends upward to maximize the diameter of the lower portion of the combustion chamber (commonly referred to as the combustion chamber major diameter D3) and the combustion chamber diameter begins to decrease to form the throat 11.
In some embodiments, the central boss 3 is located at the center of the combustion chamber, the central boss 3 is substantially circular truncated cone-shaped, the top surface of the central boss 3 may be a plane or a spherical surface, the embodiment illustrates a plane, but the present invention is not limited thereto, the central boss 3 includes a first boss, a second boss, and a third boss stacked from top to bottom, the lower portion of the third boss is connected with the bottom arc 10 in a smooth arc manner, the axial cross section of the central boss 3 includes a first boss side surface bus 5, a second boss side surface bus 7, and a third boss side surface bus 9 from top to bottom, the first boss side surface bus 5 is connected with the top surface of the central boss 3 in a smooth transition manner through a boss arc 634, the third boss side surface bus 9 is connected with the bottom arc 10 in a smooth transition manner, the first boss side surface bus 5 and the second boss side surface bus 7 are connected with the third boss side surface bus 9 in a smooth transition manner through a boss arc 638, an included angle between the first boss side surface bus 5 and the combustion chamber center line 16 of the combustion chamber is larger than an included angle between the second boss side surface bus 16 and the combustion chamber bus 3616 of the combustion chamber 16.
In some embodiments, the ratio of the distance R from the center line 16 of the combustion chamber to the maximum diameter D3 of the lower space of the combustion chamber at the intersection of the extension line of the first boss side surface generatrix 5 and the extension line of the second boss side surface generatrix 7 is between 0.05 and 0.095.
In some embodiments, the top surface of the center boss 3 is generally lower than the top surface 2 of the piston.
In summary, compared with the closest prior art, the combustion chamber of the direct injection diesel engine has the characteristics that the central boss of the combustion chamber is formed by piling three round tables, and the space of the combustion chamber is divided into an upper part and a lower part by a necking. For the upper part of the combustion chamber, the proportion of fuel steam sprayed into the upper part of the combustion chamber is reasonable through the reasonable designed circle center position and arc radius of the necking arc, the diameter of the opening at the upper part of the combustion chamber and the angle of two step straight line sections forming a step surface. After fuel steam enters the step surface, the ring surface formed by the straight line section of the first step is wider, the steam has sufficient motion space, and the included angle of the ring surface and the top surface of the piston is about 20 degrees to ensure that the steam cannot be retained on the step; the included angle of the ring surface formed by the straight line section of the second step and the top surface of the piston is about 55 degrees, the flow guiding effect on fuel steam entering the squeezing area is good, as shown in figure 4, most of the steam rushes to the bottom surface of the cylinder cover under the flow guiding of the ring surface and then is folded back to enter the squeezing area, a small part of the steam moves towards the center direction of the combustion chamber, and the rest part of the steam moves towards the direction of the cylinder wall along the direction that the ring surface climbs the top surface. Therefore, the combustion chamber has high utilization ratio on the air in the squish area, and can not enable a large amount of high-temperature gas to move to the wall surface of the cylinder.
The central boss of the combustion chamber is of a structure formed by stacking three circular truncated cones, so that a bus on the side face of the boss is not a single straight line segment any more, but is changed into a straight line segment and a transition circular arc with three segments having different included angles with the central line of the combustion chamber, and the boss structure enables fuel-air mixed gas entering the bottom of the combustion chamber to climb in a stepped manner and move towards the center and the upper part of the combustion chamber.
The foregoing descriptions of specific exemplary embodiments of the present invention have been presented for purposes of illustration and description. It is not intended to limit the invention to the precise form disclosed, and obviously many modifications and variations are possible in light of the above teaching. The exemplary embodiments were chosen and described in order to explain certain principles of the invention and its practical application to enable one skilled in the art to make and use various exemplary embodiments of the invention and various alternatives and modifications as are suited to the particular use contemplated. It is intended that the scope of the invention be defined by the claims and their equivalents.
Claims (6)
1. A combustion chamber of a direct injection diesel engine, which is located at the center or non-center of a piston top surface of a piston body and above a pin hole, wherein the combustion chamber has a radial circular shape and an axial cross-section of an omega shape, the combustion chamber comprising:
the upper step is an annular surface of the combustion chamber, which is in contact with the arc of the top surface of the piston, and the axial section of the upper step comprises a first step straight line section and a second step straight line section from top to bottom;
the necking is positioned below the upper step, is in an annular arc-shaped convex shape, and is connected with a smooth arc at the lower part of the straight line section of the second step;
the bottom arc is positioned at the bottom of the combustion chamber, the bottom arc is connected with the lower smooth arc of the necking, the bottom center of the bottom arc is a cambered surface, and the necking is connected with the outer end smooth arc of the bottom arc; and
the central boss is positioned in the center of the combustion chamber, the central boss is substantially in a shape of a circular truncated cone with an inwards concave side surface, and the central boss comprises a first boss, a second boss and a third boss which are stacked from top to bottom; the lower part of the third boss is connected with the bottom arc smooth arc;
the axial section of the central boss comprises a first boss side bus, a second boss side platform bus and a third boss side bus from top to bottom, the buses of the three bosses are concave, and the inner end of the bottom arc is smoothly connected with the third boss side bus at the lower part of the central boss;
wherein the first boss side surface bus is smoothly and transitionally connected with the top surface of the central boss through a boss arc; the side surface bus of the third boss is in smooth transition connection with the bottom arc; the first boss side surface bus and the second boss side surface bus are in smooth transition connection through a first bus transition arc; and the second boss side surface platform bus and the third boss side surface bus are in smooth transition connection through a second bus transition arc.
2. The combustion chamber of a direct injection diesel engine of claim 1 wherein said first stepped straight line segment is angled between 53 ° and 57 ° from said piston top surface, said second stepped straight line segment is angled between 18 ° and 22 ° from said piston top surface, and said first stepped straight line segment is joined to said second stepped straight line segment by a smooth circular arc.
3. The combustion chamber of a direct injection diesel engine as set forth in claim 1, characterized in that the ratio of the distance of the center of the circular arc of the throat from the top face of the piston to the depth of the combustion chamber is between 0.35 and 0.45; the ratio of the maximum opening diameter of the top of the first step straight-line section to the minimum diameter of the necking is 1.30-1.32.
4. The combustion chamber of a direct injection diesel engine of claim 1 wherein the angle between the first boss side generatrix and the combustion chamber centerline is greater than the angle between the second boss side generatrix and the combustion chamber centerline, and the angle between the first boss side generatrix and the combustion chamber centerline is less than the angle between the third boss side generatrix and the combustion chamber centerline.
5. The combustion chamber of a direct injection diesel engine according to claim 1, wherein a ratio of a distance from a center line of the combustion chamber to a maximum diameter of a lower space of the combustion chamber at an intersection of an extension line of the first boss side surface generatrix and an extension line of the second boss side surface base generatrix is 0.05 to 0.095.
6. The combustion chamber of a direct injection diesel engine as set forth in claim 1 wherein the top surface of said center boss is lower than the top surface of said piston.
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| 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 |
| CN115822803B (en) * | 2023-01-06 | 2023-06-23 | 潍柴动力股份有限公司 | Piston and engine |
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| CN103782004A (en) * | 2011-09-05 | 2014-05-07 | 五十铃自动车株式会社 | Direct-injection engine combustion chamber structure |
| JP2016125422A (en) * | 2015-01-05 | 2016-07-11 | いすゞ自動車株式会社 | Combustion chamber structure of direct injection type engine |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| JP2011117319A (en) * | 2009-12-01 | 2011-06-16 | Mitsubishi Fuso Truck & Bus Corp | Combustion chamber structure of direct injection diesel engine |
| CN201739005U (en) * | 2010-07-08 | 2011-02-09 | 中国汽车工程研究院股份有限公司 | Low-emission combustion chamber of vehicle direct-injection diesel |
| JP5786956B2 (en) * | 2011-12-16 | 2015-09-30 | トヨタ自動車株式会社 | Combustion chamber structure of internal combustion engine |
| AT518516B1 (en) * | 2016-03-10 | 2018-03-15 | Avl List Gmbh | PISTON FOR A AIR COMPRESSIVE INTERNAL COMBUSTION ENGINE |
| 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 |
| CN108518287A (en) * | 2018-03-29 | 2018-09-11 | 天津中恒动力研究院有限公司 | Piston and engine assembly |
| CN209067353U (en) * | 2018-12-10 | 2019-07-05 | 广西玉柴机器股份有限公司 | The combustion chamber of diesel engine with direct injection |
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Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103782004A (en) * | 2011-09-05 | 2014-05-07 | 五十铃自动车株式会社 | Direct-injection engine combustion chamber structure |
| JP2016125422A (en) * | 2015-01-05 | 2016-07-11 | いすゞ自動車株式会社 | Combustion chamber structure of direct injection type engine |
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