CN111365139A - Cylinder head and internal combustion engine - Google Patents
Cylinder head and internal combustion engine Download PDFInfo
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- CN111365139A CN111365139A CN201811593378.1A CN201811593378A CN111365139A CN 111365139 A CN111365139 A CN 111365139A CN 201811593378 A CN201811593378 A CN 201811593378A CN 111365139 A CN111365139 A CN 111365139A
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- cylinder
- cylinder head
- combustion chamber
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- air inlet
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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
- F02F1/00—Cylinders; Cylinder heads
- F02F1/24—Cylinder heads
- F02F1/42—Shape or arrangement of intake or exhaust channels in cylinder heads
- F02F1/4285—Shape or arrangement of intake or exhaust channels in cylinder heads of both intake and exhaust channel
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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
- F02B23/08—Other engines characterised by special shape or construction of combustion chambers to improve operation with positive ignition
- F02B23/10—Other engines characterised by special shape or construction of combustion chambers to improve operation with positive ignition with separate admission of air and fuel into cylinder
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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
- F02B23/08—Other engines characterised by special shape or construction of combustion chambers to improve operation with positive ignition
- F02B23/10—Other engines characterised by special shape or construction of combustion chambers to improve operation with positive ignition with separate admission of air and fuel into cylinder
- F02B2023/106—Tumble flow, i.e. the axis of rotation of the main charge flow motion is horizontal
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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)
- Cylinder Crankcases Of Internal Combustion Engines (AREA)
Abstract
The invention provides a cylinder cover and an internal combustion engine, wherein the cylinder cover is arranged on a cylinder body of the internal combustion engine and comprises a cylinder cover combustion chamber, an air inlet channel and an air outlet channel, and a preset air inlet area and a preset air outlet area are arranged in an enveloping space of the cylinder cover combustion chamber; the air inlet channel is provided with a plurality of air inlets communicated with the air inlet area; the exhaust passage is provided with a plurality of exhaust ports communicated with the exhaust area; the side walls of the combustion chamber of the cylinder cover, which are positioned on two sides of the central plane, are asymmetrically arranged by taking the central plane of the air inlet covering total area and the central plane of the air outlet covering total area as a boundary. According to the cylinder cover, the flow direction of gas around the peripheral wall of the combustion chamber in the air inlet process can be changed through the asymmetric structure of the side wall of the combustion chamber of the cylinder cover, so that the oil-gas mixing in the cylinder is promoted.
Description
Technical Field
The invention relates to the technical field of internal combustion engines, in particular to a cylinder cover. Meanwhile, the invention also relates to an internal combustion engine applying the cylinder cover.
Background
The internal combustion engine invented by german inventor in 1876 was, through more than 140 years of development, now intimately incorporated into people's daily lives as a machine to provide a stable source of power for vehicles. With the continuous development of the reform and the opening of China and the comprehensive improvement of national economy, the popularization rate of the internal combustion engine as a power source of a passenger vehicle is increased year by year, and the air quality is reduced year by year.
Automobile exhaust emission is one of air pollution sources, slowly enters the public visual field and is widely concerned by all social circles. Although the scientific community has not been made a unified conclusion about whether the atmospheric haze is related to the automobile exhaust emission or not at present, the development direction of automobile exhaust cleaning becomes a consensus of the whole society. Meanwhile, to cope with global climate change after 2020, nearly 200 contracting parties (including China) agreed to pass through Paris protocol in Paris, France, and United nations climate change frame convention in 2015. The agreement states that parties will enforce global response to the threat of climate change, controlling greenhouse gas emissions as soon as possible. CO 22Its emissions are increasingly gaining attention as a major greenhouse gas.
It is known that the fuel of internal combustion engines is mainly petroleum derivatives, the main component of which comprises C, the combustion of which necessarily produces CO2. Desire to reduce CO2The main approach of emission is to improve the thermal efficiency of the engine, and the current mainstream measures adopt a supercharged direct injection internal combustion engine which has a certain emission reduction effect by means of internal combustion engine supercharging miniaturization and direct injection in an auxiliary cylinder.
However, the current supercharged direct-injection internal combustion engine generally adopts a cylinder gas flow mode in a tumble flow mode, and an oil injector is arranged between two intake valves. The arrangement position of the oil injector and the gas flowing mode in the cylinder are not beneficial to the mixing of oil gas, and the mixed gas around a spark plug is too rich at the moment of ignition, so that the problems of incomplete combustion, excessive particulate matter emission and the like can be caused.
Disclosure of Invention
In view of the above, the present invention is directed to a cylinder head to overcome the disadvantage of the conventional structure that is not favorable for oil-gas mixing.
In order to achieve the purpose, the technical scheme of the invention is realized as follows:
a cylinder head that is provided on a cylinder block of an internal combustion engine, the cylinder head comprising:
the cylinder cover combustion chamber is internally provided with a preset air inlet area and a preset air exhaust area;
the air inlet channel is provided with a plurality of air inlets communicated with the air inlet area;
the exhaust passage is provided with a plurality of exhaust ports communicated with the exhaust area;
and the side walls of the combustion chamber of the cylinder cover, which are positioned on two sides of the central plane, are asymmetrically arranged by taking the central plane passing through the center of the total area covered by the air inlet and the center of the total area covered by the air outlet as a boundary.
Furthermore, the side wall of the cylinder cover combustion chamber, which is positioned on two sides of the central plane, is provided with a guide wall with a linear cross section, and two ends of the guide wall respectively extend to the air intake area and the air exhaust area.
Furthermore, relative to the side wall provided with the guide wall, the cross section of the other side wall is in an arc shape with a convex middle part.
Furthermore, an included angle is formed between the plane where the guide wall is located and the central plane.
Further, the range of the included angle is 0-20 degrees.
Further, a fuel injector mounting hole is formed in the cylinder head between the two air inlets, and the fuel injector mounting hole is arranged close to the side wall of the cylinder head combustion chamber.
Further, a spark plug mounting hole is formed in a central portion of the cylinder head in a region corresponding to the cylinder head combustion chamber.
Further, the air inlet channel is configured at one side of the cylinder cover corresponding to the air inlet area, the air inlet channel is provided with two air inlet ports, and the two air inlet ports are symmetrically arranged around the central plane; the exhaust passage is configured on one side of the cylinder head corresponding to the exhaust area, the exhaust passage has two air outlets, and the two air outlets are symmetrically arranged about the central plane.
Further, an intake valve for opening and closing the intake port is disposed in the intake duct, and an exhaust valve for opening and closing the exhaust port is disposed in the exhaust duct.
Compared with the prior art, the invention has the following advantages:
according to the cylinder cover, the flow direction of gas around the peripheral wall of the combustion chamber in the air inlet process can be changed through the asymmetric structure of the side wall of the combustion chamber of the cylinder cover, namely, the movement perpendicular to the movement direction of the tumble flow is added on the basis of the original tumble flow, so that the oil-gas mixing in the cylinder is promoted, and the cylinder cover has good practicability.
Another object of the present invention is to provide an internal combustion engine, which includes a cylinder block, and the cylinder head is disposed on the cylinder block.
Compared with the prior art, the internal combustion engine has the same beneficial effects as the cylinder cover, and the detailed description is omitted.
Drawings
The accompanying drawings, which are included to provide a further understanding of the invention, are incorporated in and constitute a part of this specification, illustrate embodiments of the invention and together with the description serve to explain the invention and not to limit the invention. In the drawings:
fig. 1 is a partial schematic structural view of a cylinder head according to a first embodiment of the present invention;
FIG. 2 is a cross-sectional view A-A of FIG. 1;
FIG. 3 is a cross-sectional view B-B of FIG. 1;
FIG. 4 is an enlarged view of a portion of FIG. 1;
FIG. 5 is a schematic view of the structure of FIG. 4 from another perspective;
FIG. 6 is a schematic view showing a structure in which the flow direction of gas in the combustion chamber exhibits tumble flow;
FIG. 7 is a schematic view showing the flow direction of gas in the combustion chamber at a position close to the inner wall;
FIG. 8 is a schematic view showing the structure of the gas flow direction in the combustion chamber at a position close to the center;
FIG. 9 is a schematic view showing a structure in which the flow direction of gas in the combustion chamber exhibits a vortex;
description of reference numerals:
1-a cylinder cover combustion chamber, 2-an air inlet, 3-an exhaust port, 4-an oil injector mounting hole, 5-a spark plug mounting hole, 6-a guide wall, 7-a section, 8-a cylinder hole, 9-a piston and 10-a piston rod;
201-intake zone, 301-exhaust zone.
Detailed Description
It should be noted that the embodiments and features of the embodiments may be combined with each other without conflict.
In the description of the present invention, it should be noted that the terms "upper", "lower", "left", "right", and the like indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings, and are only for convenience of describing the present invention and simplifying the description, but do not indicate or imply that the referred device or element must have a specific orientation, be constructed in a specific orientation, and be operated, and thus, should not be construed as limiting the present invention.
The present invention will be described in detail below with reference to the embodiments with reference to the attached drawings.
Example one
The present embodiment relates to a cylinder head, as shown in fig. 1 to 4, which is provided on a cylinder block of an internal combustion engine, not shown, and in which a cylinder head combustion chamber 1, and an intake passage and an exhaust passage are formed.
Although only one cylinder head combustion chamber 1 is shown in fig. 1, the number of cylinder head combustion chambers 1 corresponds to the number of cylinders of the internal combustion engine in actual installation, and reference may be made to the conventional structure of the internal combustion engine. In the cylinder head combustion chamber 1, a predetermined intake area 201 and an exhaust area 301 are provided in the enclosed space, and as shown in fig. 4 to 5, a plane passing through the center line a and perpendicular to the center line b is defined as a boundary, the upper space constitutes the intake area 201, and the lower space constitutes the exhaust area 301.
To facilitate the detailed description of the structure of the cylinder head, the structure of the combustion chamber will be described below with reference to fig. 7, and fig. 7 is a schematic diagram of the structure cut along the axis of the cylinder. The upper part is in the shape of a cylinder cover combustion chamber 1 in a cylinder, the lower part is in the shape of a cylinder hole 8 in the cylinder, a piston 9 which slides up and down along the cylinder hole 8 and a piston rod 10 which is fixedly connected to the lower end of the piston 9 are arranged in the cylinder hole 8. In an internal combustion engine, the combustion chamber is an area defined by a recess in the lower surface of the cylinder head, the upper portion of the inner wall of the cylinder bore 8, and the position of the upper end surface when the piston 9 moves to the top dead center. The dimples on the lower surface of the cylinder are conventionally referred to as head combustion chambers 1.
Further, an intake port and an exhaust port, not shown, are provided in the cylinder head, an intake valve for opening and closing the intake port 2 is provided in the intake port, and an exhaust valve for opening and closing the exhaust port 3 is provided in the exhaust port. The air inlet channel is arranged on one side of the cylinder cover corresponding to the air inlet area 201, one end of the air inlet channel is provided with a plurality of air inlets 2 communicated with the air inlet area 201, and the other end of the air inlet channel is arranged on one side of the cylinder cover; the exhaust passage is arranged on one side of the cylinder head corresponding to the exhaust area 301, and one end of the exhaust passage is provided with a plurality of exhaust ports 3 communicated with the exhaust area 301, and the other end of the exhaust passage is arranged on the other side of the cylinder head.
During the use of the internal combustion engine, when the left intake valve and the right intake valve are opened in the intake stroke, fresh air can enter the cylinder head combustion chamber 1 from the left intake port 2 and the right intake port 2. The left and right intake valves are poppet valves that increase or decrease the opening area by a change in the opening lift.
Based on the above description of the overall structure, the main improvement of the present embodiment is that the side walls of the head combustion chamber 1 on both sides of the center plane are asymmetrically arranged, with the center of the total area covered by the intake port 2 and the center plane of the total area covered by the exhaust port 3 being the boundary.
Specifically, as shown in fig. 4, in the present embodiment, each intake port has two intake ports 2, and each exhaust port has two exhaust ports 3. The sum of the coverage areas of the two air inlets 2 is the center of the total coverage area of the air inlets 2, that is, the two air inlets 2 are symmetrically arranged about a central plane, and the sum of the coverage areas of the two air outlets 3 is the center of the total coverage area of the air outlets 3, that is, the two air outlets 3 are also symmetric about the central plane. If each exhaust duct has one inlet port 2 and each exhaust duct also has one outlet port 3, the inlet port 2 covers the center of the total area as the center of the inlet port 2, and the outlet port 3 covers the center of the total area as the center of the outlet port 3. Therefore, the central plane in which the air intake port 2 covers the center of the total area and the air exhaust port 3 covers the center of the total area is a plane perpendicular to the center line a and passing through the center line b.
It should be noted that, in the combustion chamber with the above structure, the upper portion of fig. 4 corresponds to the left portion of fig. 6, as shown by fig. 4 in combination with fig. 6, in practical application, the gas flow direction entering the combustion chamber may be as shown in fig. 6, and the gas flow direction substantially flows according to the gas flow path c shown in fig. 6, that is, the so-called tumble flow, and the flow direction in the cylinder head combustion chamber 1 substantially flows from the intake area 201 to the exhaust area 301.
In addition, in order to facilitate the oil-gas mixture, an injector mounting hole 4 is formed in the cylinder head between the two intake ports 2, and the injector mounting hole 4 is arranged near a side wall of the cylinder head combustion chamber 1, and a spark plug mounting hole 5 is formed in a central portion of the cylinder head corresponding to a region of the cylinder head combustion chamber 1. In addition, the mounting positions of the injector mounting hole 4 and the plug mounting hole 5 may be set to other positions with reference to the related art.
In order to promote the gas mixing in the combustion chamber, as shown in fig. 4 and 5, of the side walls of the cylinder head combustion chamber 1 located on both sides of the center plane, that is, the side walls on both sides of the left side and the right side shown in fig. 4, the cross section of the side wall on the left side is an arc shape with a convex middle part, the side wall on the right side is provided with a guide wall 6 with a straight line-shaped cross section, and both ends of the guide wall 6 respectively extend to the intake area 201 and the exhaust area 301, which is substantially equivalent to adding the guide wall 6 on the basis of the side wall of the cylinder head combustion chamber 1 in the prior art, so that the distance between the side wall on the right side and the intake port 2 on the right side of the cylinder head.
Still referring to fig. 4, when the opening lift of the left and right intake ports 2, 2 is small, the range of the intake direction at the left intake port 2 is a left fan-shaped region that is clockwise rotated from the injector mounting hole 4 to the circular arc-shaped side wall of the combustion chamber around the left intake port 2, and the range of the intake direction at the right intake port 2 is a right fan-shaped region that is counterclockwise rotated from the injector mounting hole 4 to the guide wall 6 around the right intake port 2, and the specific flow direction may be the direction indicated by the arrow that shows the gas flow direction with reference to the intake port 2 region in fig. 4. At this time, when the intake valve lift is small, the remaining intake ranges of the left and right intake ports 2 and 2 are blocked by the side wall of the cap combustion chamber, and the intake air is temporarily ignored.
Referring to fig. 4 in conjunction with fig. 8, the intake air component of the left intake port 2 in the range from the injector mounting hole 4 to the left exhaust port 3, which is directed from the left exhaust port 3 to the right exhaust port 3, and the intake air component of the right intake port 2 in the range from the injector mounting hole 4 to the right exhaust port 3, which is directed from the right exhaust port 3 to the left exhaust port 3, cancel each other out, and this part of intake air does not generate a swirling motion of the gas in the cylinder along the axis of the cylinder hole, and the horizontal acting forces of the left gas flow path f and the right gas flow path g shown in fig. 8 cancel each other out.
Still referring to fig. 4 in combination with fig. 7, the intake air of the left side intake port 2 in the range that the left side exhaust port 3 rotates clockwise along the axis of the left side intake port 2 to the arc-shaped side wall of the combustion chamber is guided by the arc-shaped side wall, so that the intake air component quantity directed from the left side exhaust port 3 to the right side exhaust port 3 is generated, and the gas flow direction flows according to the flow path d; the intake air in the range that the right side intake port 2 rotates counterclockwise along the right side intake port 2 to the guide wall 6 at the right side exhaust port 3 is guided by the guide wall 6 to generate an intake air component amount in the direction from the right side exhaust port 3 to the left side exhaust port 3, and the air flows along the flow path e.
Because the left air inlet 2 is far away from the arc wall surface of the cylinder head combustion chamber 1 and the right air inlet 2 is near to the guide wall 6, the air inlet of the left air inlet 2 in the range that the left air outlet 3 rotates clockwise along the axis of the left air inlet 2 to the arc side wall of the combustion chamber has the air inlet component amount which is from the left air outlet 3 to the right air outlet 3, and the air inlet component amount which is smaller than the air inlet of the right air inlet 2 in the range that the right air outlet 3 rotates anticlockwise along the right air inlet 2 to the guide wall 6 has the air inlet component amount from the right air outlet 3 to the left air outlet 3, so that the air inlet component amount which is from the right air outlet 3 to the right air outlet 3 is generated in the cylinder, the cylinder hole generates the driving force of the vortex motion rotating along the axis, and the gas flow direction moves according to the, that is, the vortex, and then make the gas that gets into in the cylinder increase the vortex on original tumble basis to effectively promote the interior oil gas of cylinder and mix.
At left side air inlet 2, when the lift is great is opened to right side air inlet 2, because of left side admission valve and the right side admission valve respectively apart from the distance of the air inlet 2 of the corresponding side far away, admit air and do not receive the blockking of 1 lateral wall of cylinder cap combustion chamber, the scope of the direction of admitting air of left side air inlet 2 and right side air inlet 2 department all is the circumferencial direction of whole left side air inlet 2 and right side air inlet 2, and the momentum of admitting air of the left side air inlet 2 in the 3 directions of directional right side gas vent 3 of left side gas vent 3 and the momentum size of admitting air of the right side gas inlet 2 in the 3 directions of the gas vent 3 that. The intake air of the left intake port 2 and the intake air of the right intake port 2 generate an intake air momentum in the direction of the exhaust area 301 in the intake area 201, and at this time, the cylinder interior gas is mainly caused to generate a tumble motion as shown in fig. 6.
Since the combustion speed of the internal combustion engine is positively correlated with the turbulence intensity in the cylinder at the time of ignition, and the swirl motion is not like the tumble motion, it can be crushed into small turbulence near the top dead center of the piston 9, thereby increasing the turbulence intensity in the cylinder. Therefore, the strength of the vortex in the internal combustion engine is not suitable to be too high, and the scheme of the embodiment that the guide wall 6 is arranged in the cylinder cover combustion chamber 1 can generate the vortex mainly when the left air inlet 2 and the right air inlet 2 have small lift ranges, and has no influence on the tumble motion under the condition of large lift range, so that the whole tumble motion in the cylinder can not be influenced, and the requirement of the combustion of the internal combustion engine on the gas flow form in the cylinder is met.
In order to ensure that the guide wall 6 has a sufficient guiding effect on the intake air, it is not suitable to be arranged too far away from the left-hand intake opening 2 or the right-hand intake opening 2.
The guide wall 6 is provided at the right side intake port 2 as an example. If the guide wall 6 is disposed far from the right intake port 2, the difference between the intake air component amount directed from the right exhaust port 3 to the left exhaust port 3 by the right intake port 2 in the range where the right exhaust port 3 rotates counterclockwise along the right intake port 2 to the guide wall 6 is small because of the guide wall 6, and the intake air component amount directed from the left exhaust port 3 to the right exhaust port 3 by the left intake port 2 in the range where the left exhaust port 3 rotates clockwise along the axis of the left intake port 2 to the circular arc-shaped side wall of the combustion chamber is guided by the circular arc-shaped side wall. In this case, the intake momentum from the right exhaust port 3 to the right exhaust port 3 in the cylinder is too small, and although the swirl motion can be generated, the swirl motion intensity is too low to achieve the effect of homogenizing the air mixture in the cylinder, so the distance from the guide wall 6 to the left air inlet 2 or the right air inlet 2 is generally set to be less than or equal to 3 mm.
In order to ensure the working reliability of the left air inlet 2 and the right air inlet 2, the guide wall 6 is not too close to the left air inlet 2 or the right air inlet 2.
The guide wall 6 is provided at the right side intake port 2 as an example. Because the right side air inlet 2 and the cylinder cover are in clearance fit, the right side air inlet 2 can have certain amplitude of vibration in the opening/closing process. If the guide wall 6 is provided closer to the right intake port 2, there is a risk that the right intake port 2 interferes with the guide wall 6, and the structure of the cross section 7 of the guide wall 6 shown in fig. 5, that is, the structure formed to prevent interference with the guide wall 6.
It should also be noted here that the guide wall 6 may be cast integrally with the cylinder head, or may be formed by post-machining, such as welding a guide plate, or by removing material. However, because the air inlet structures and the oil injectors of different models are arranged differently, the severity of the unevenness of the mixed gas in the cylinder is different, and the required vortex intensity of the even mixed gas is different. When a smaller swirl strength is required, the guide wall 6 may be cast integrally with the cylinder head, in which case the minimum distance between the guide wall 6 and the left-side intake port 2 or the right-side intake port 2 may be set to 0.5mm in general in order to tolerate casting tolerances. When a large swirl strength is required, it can be formed by a material removal process, and since the tolerance of the material removal process is smaller than the casting tolerance, the minimum distance between the guide wall 6 and the left or right inlet port 2 can be set to 0.2 mm.
However, according to the analysis of the gas flow in the cylinder, the included angle α can be set to range from 0 ° to 20 °, preferably from 8 ° to 10 °, for better uniform gas-oil mixing in the cylinder without affecting the turbulence intensity at the time of ignition, and the inclined manner is preferably the inclined manner shown in fig. 4, in which the upper portion of the guide wall 6 is inclined to the right in the state shown in fig. 4, so that the distance from the gas inlet 2 to the guide wall 6 is substantially close to the distance from the gas outlet 3 to the guide wall 6, in order to quickly guide the right-side gas flow from the gas inlet area 201 to the gas outlet area 301, and in order to promote quick uniform gas-oil mixing in the cylinder.
In the above structure, still referring to fig. 4, the guide wall 6 is provided close to the right-side intake port 2, and besides, it may be provided close to the left-side intake port 2.
The cylinder cover of the invention adds vortex motion on the basis of tumble flow in the combustion chamber, can solve the problem that the mixed gas around a spark plug is too rich at the ignition moment of a direct injection internal combustion engine in the combustion chamber, and prevents the problems of incomplete combustion, overproof particulate matter emission and the like.
In addition, the cylinder cover can be formed by casting or machining, has a simple structure and strong applicability, does not need to add special parts, has no influence on the production and the manufacture of an internal combustion engine, and has better practicability.
Example two
The embodiment relates to an internal combustion engine, which comprises a cylinder body, wherein a cylinder cover is arranged on the upper cover of the cylinder body.
The internal combustion engine of the embodiment can promote the oil-gas in the cylinder to be quickly mixed at the ignition moment and reduce the pollutant emission by adopting the cylinder cover of the first embodiment.
The above description is only for the purpose of illustrating the preferred embodiments of the present invention and is not to be construed as limiting the invention, and any modifications, equivalents, improvements and the like that fall within the spirit and principle of the present invention are intended to be included therein.
Claims (10)
1. A cylinder head that is provided on a cylinder block of an internal combustion engine, characterized by comprising:
the cylinder cover combustion chamber (1), wherein a preset air inlet area (201) and an air exhaust area (301) are arranged in an enveloping space of the cylinder cover combustion chamber (1);
the air inlet channel is provided with a plurality of air inlets (2) communicated with the air inlet area (201);
an exhaust passage having a plurality of exhaust ports (3) communicating with the exhaust zone (301);
the side walls of the cylinder head combustion chamber (1) located on two sides of the central plane are asymmetrically arranged by taking the central plane passing through the center of the total area covered by the air inlet (2) and the central plane passing through the center of the total area covered by the air outlet (3) as a boundary.
2. The cylinder head of claim 1, wherein: the cylinder cover combustion chamber (1) is positioned in the side walls on two sides of the central plane, the side wall of one cylinder cover combustion chamber is provided with a guide wall (6) with a linear cross section, and two ends of the guide wall (6) respectively extend to the air inlet area (201) and the air exhaust area (301).
3. The cylinder head of claim 2, wherein: relative to the side wall provided with the guide wall (6), the cross section of the other side wall is in an arc shape with a convex middle part.
4. The cylinder head of claim 2, wherein: an included angle is formed between the plane of the guide wall (6) and the central plane.
5. The cylinder head of claim 4, wherein: the range of the included angle is 0-20 degrees.
6. The cylinder head of claim 1, wherein: and a fuel injector mounting hole (4) is formed between the two air inlets (2) of the cylinder cover, and the fuel injector mounting hole (4) is arranged close to the side wall of the cylinder cover combustion chamber (1).
7. The cylinder head of claim 1, wherein: the central part of the cylinder head corresponding to the area of the cylinder head combustion chamber (1) is provided with a spark plug mounting hole (5).
8. The cylinder head of claim 1, wherein: the intake passage is configured on one side of the cylinder head corresponding to the intake area (201), the intake passage is provided with two intake ports (2), and the two intake ports (2) are symmetrically arranged around the central plane; the exhaust passage is configured on one side of the cylinder cover corresponding to the exhaust area (301), the exhaust passage is provided with two air outlets, and the two air outlets are symmetrically arranged around the central plane.
9. The cylinder head according to any one of claims 1 to 8, wherein: an intake valve for opening and closing the intake port (2) is disposed in the intake passage, and an exhaust valve for opening and closing the exhaust port (3) is disposed in the exhaust passage.
10. An internal combustion engine including a cylinder block, characterized in that: the cylinder head according to any one of claims 1 to 9 is provided to the cylinder block upper cover.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201811593378.1A CN111365139A (en) | 2018-12-25 | 2018-12-25 | Cylinder head and internal combustion engine |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201811593378.1A CN111365139A (en) | 2018-12-25 | 2018-12-25 | Cylinder head and internal combustion engine |
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| CN111365139A true CN111365139A (en) | 2020-07-03 |
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| CN201811593378.1A Pending CN111365139A (en) | 2018-12-25 | 2018-12-25 | Cylinder head and internal combustion engine |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114810409A (en) * | 2022-05-10 | 2022-07-29 | 潍柴动力股份有限公司 | Cylinder head and engine assembly |
Citations (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4706623A (en) * | 1984-05-22 | 1987-11-17 | Saab-Scania Altoebplag | Cylinder head for an internal combustion engine |
| US5582147A (en) * | 1994-04-25 | 1996-12-10 | Hyundai Motor Company | Combustion chamber for internal combustion engine having multiple valves |
| CN1176338A (en) * | 1996-08-12 | 1998-03-18 | 马自达汽车株式会社 | Direct fuel injection engine |
| CN1840891A (en) * | 2005-03-28 | 2006-10-04 | 日产自动车株式会社 | Multi-spot combustion engine |
| CN201206502Y (en) * | 2008-04-22 | 2009-03-11 | 奇瑞汽车股份有限公司 | Small-sized petrol engine cylinder cover |
| CN201246211Y (en) * | 2008-08-27 | 2009-05-27 | 重庆宗申发动机制造有限公司 | Motorcycle engine combustion chamber |
| CN104033233A (en) * | 2013-03-08 | 2014-09-10 | 铃木株式会社 | Combustion Chamber Structure Of Internal-combustion Engine |
| CN204344331U (en) * | 2014-11-27 | 2015-05-20 | 上海通用汽车有限公司 | Car engine air admittance combustion system, motor car engine and automobile |
| CN108869006A (en) * | 2018-06-20 | 2018-11-23 | 奇瑞汽车股份有限公司 | Small-displacement gasoline engine combustion system |
| CN209195567U (en) * | 2018-12-29 | 2019-08-02 | 重庆长安汽车股份有限公司 | A kind of pressurization direct-injection Miller cycle gasoline engine cylinder cover structure and automobile |
-
2018
- 2018-12-25 CN CN201811593378.1A patent/CN111365139A/en active Pending
Patent Citations (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4706623A (en) * | 1984-05-22 | 1987-11-17 | Saab-Scania Altoebplag | Cylinder head for an internal combustion engine |
| US5582147A (en) * | 1994-04-25 | 1996-12-10 | Hyundai Motor Company | Combustion chamber for internal combustion engine having multiple valves |
| CN1176338A (en) * | 1996-08-12 | 1998-03-18 | 马自达汽车株式会社 | Direct fuel injection engine |
| CN1840891A (en) * | 2005-03-28 | 2006-10-04 | 日产自动车株式会社 | Multi-spot combustion engine |
| CN201206502Y (en) * | 2008-04-22 | 2009-03-11 | 奇瑞汽车股份有限公司 | Small-sized petrol engine cylinder cover |
| CN201246211Y (en) * | 2008-08-27 | 2009-05-27 | 重庆宗申发动机制造有限公司 | Motorcycle engine combustion chamber |
| CN104033233A (en) * | 2013-03-08 | 2014-09-10 | 铃木株式会社 | Combustion Chamber Structure Of Internal-combustion Engine |
| CN204344331U (en) * | 2014-11-27 | 2015-05-20 | 上海通用汽车有限公司 | Car engine air admittance combustion system, motor car engine and automobile |
| CN108869006A (en) * | 2018-06-20 | 2018-11-23 | 奇瑞汽车股份有限公司 | Small-displacement gasoline engine combustion system |
| CN209195567U (en) * | 2018-12-29 | 2019-08-02 | 重庆长安汽车股份有限公司 | A kind of pressurization direct-injection Miller cycle gasoline engine cylinder cover structure and automobile |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114810409A (en) * | 2022-05-10 | 2022-07-29 | 潍柴动力股份有限公司 | Cylinder head and engine assembly |
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