Intake system and engine having the same

Abstract

The application discloses an air intake system and an engine with the same. The air intake system is used for an engine, and the air intake system has a pressure stabilizing cavity and an air intake passage. The air intake passage comprises an air intake section, a connecting section and an air outlet section. The connecting section is connected between the air intake section and the air outlet section. The air intake section has an air inlet at one end away from the connecting section. The air inlet is communicated with the pressure stabilizing cavity. In the direction of the connecting section to the pressure stabilizing cavity, the flow area of the air intake section gradually increases, which is beneficial to improve the gas flow rate of the pressure stabilizing cavity into the air intake passage, so as to improve the air intake flow rate of the cylinder. The air outlet section has an air outlet at one end away from the connecting section. The air outlet is adapted to be communicated with the cylinder of the engine. The connecting section is configured as a downward bending angle structure. When the gas flows through the connecting section, the gas can flow to the upper space of the air outlet section, so as to be beneficial to increase the gas flow rate from the upper space of the air outlet into the cylinder, and thus be beneficial to improve the tumble flow intensity.

Description

Technical Field

[0001] This invention relates to the field of engine technology, and more specifically, to an intake system and an engine having the same. Background Technology

[0002] When designing the intake system of an engine, the intake port is usually designed to face upwards at an angle to maximize the cross-sectional area of ​​the intake port, reduce flow resistance, and increase intake flow. However, when the gas flows from the intake valve into the cylinder, the intake volume above and below the intake valve is similar, which is not conducive to improving the tumble intensity.

[0003] In related technologies, in order to improve the tumble flow intensity, the cross-sectional area of ​​the intake passage can be reduced to increase the gas flow rate and enhance the tumble flow, or the direction of the intake passage can be changed to increase the fish belly-shaped structure to make the gas distribution uneven, so that most of the gas enters the cylinder from the upper part of the intake valve. However, all of the above methods will cause an increase in gas flow resistance and a decrease in gas flow rate. Summary of the Invention

[0004] The present invention aims to at least partially solve one of the aforementioned technical problems in the prior art. To this end, the present invention proposes an intake system that can improve intake flow rate and tumble intensity.

[0005] The present invention also proposes an engine having the above-described intake system.

[0006] An intake system according to an embodiment of the present invention is used in an engine. The intake system has a pressure regulating chamber and an intake passage. The intake passage includes an intake section, a connecting section, and an exhaust section. The connecting section connects the intake section and the exhaust section. The intake section has an intake port at one end away from the connecting section, and the intake port communicates with the pressure regulating chamber. The flow area of ​​the intake section gradually increases in the direction from the connecting section to the pressure regulating chamber. The exhaust section has an exhaust port at one end away from the connecting section, and the exhaust port is adapted to communicate with a cylinder of the engine. On the orthographic projection plane of the intake system, the extension line of the centerline of the intake section and the extension line of the centerline of the exhaust section intersect at point A. Point A is located within the orthographic projection of the connecting section, and the centerlines of the intake section and the exhaust section are both located below point A.

[0007] According to the air intake system of the present invention, the air intake duct and the pressure regulating chamber are integrated into one unit. The air intake duct includes an intake section, a connecting section and an outlet section. In the direction from the connecting section to the pressure regulating chamber, the flow area of ​​the intake section gradually increases, which is beneficial to increasing the gas flow rate from the pressure regulating chamber into the air intake duct, thereby increasing the air intake flow rate of the cylinder. The connecting section is constructed with a downward bend, so that when the gas flows through the connecting section, it can flow into the upper space of the outlet section, which is beneficial to increasing the gas flow rate from the upper space of the outlet into the cylinder, thereby improving the tumble intensity.

[0008] According to some embodiments of the present invention, on the orthographic projection plane of the intake system, the angle formed by the extension of the centerline of the intake section and the extension of the centerline of the exhaust section is α and satisfies the relationship: 130°≤α≤170°.

[0009] According to some embodiments of the present invention, the distance between point A and the center line of the cylinder is L1 and satisfies the relationship: 40mm≤L1≤60mm.

[0010] According to some embodiments of the present invention, the distance between point A and the air inlet is L2 and satisfies the relationship: 35mm≤L2≤55mm.

[0011] According to some embodiments of the present invention, on the orthographic projection plane of the intake system, the angle formed by the centerline of the exhaust section and the centerline of the cylinder is β and satisfies the relationship: 45°≤β≤50°.

[0012] According to some embodiments of the present invention, the lower wall surface adjacent to the air outlet section is a plane.

[0013] According to some embodiments of the present invention, the angle between the lower wall surface of the air outlet section adjacent to the air outlet and the plane where the air outlet is located is γ and satisfies the relationship: 25°≤γ≤30°.

[0014] According to some embodiments of the present invention, the angle between the upper wall of the air intake section and the plane where the air intake is located is δ and satisfies the relationship: 84°≤δ≤86°; the angle between the lower wall of the air intake section and the plane where the air intake is located is ε and satisfies the relationship: 54°≤ε≤56°.

[0015] According to some embodiments of the present invention, there are multiple air intake channels, and the flow area of ​​the pressure stabilizing cavity gradually increases along the arrangement direction of the air intake channels, and the side with the largest flow area of ​​the pressure stabilizing cavity has a total air intake inlet.

[0016] According to some embodiments of the present invention, the top-view angle of the air intake is η and satisfies the relationship: η≤10°.

[0017] According to another embodiment of the present invention, the engine includes a cylinder head having the above-described intake system.

[0018] According to an embodiment of the engine, the intake manifold and the pressure regulating chamber are integrated into one unit. The intake manifold includes an intake section, a connecting section, and an outlet section. In the direction from the connecting section to the pressure regulating chamber, the flow area of ​​the intake section gradually increases, which is beneficial to increasing the gas flow rate from the pressure regulating chamber into the intake manifold, thereby increasing the intake flow rate of the cylinder. The connecting section is constructed with a downward bend, so that when the gas flows through the connecting section, it can flow into the upper space of the outlet section, which is beneficial to increasing the gas flow rate from the upper space of the outlet into the cylinder, thereby improving the tumble intensity.

[0019] Additional aspects and advantages of the invention will be set forth in part in the description which follows, and in part will be obvious from the description, or may be learned by practice of the invention. Attached Figure Description

[0020] Figure 1 This is a front view of the intake system according to an embodiment of the present invention;

[0021] Figure 2 This is a top view of the intake system according to an embodiment of the present invention.

[0022] Figure label:

[0023] Pressure regulating chamber 1; Main air inlet 11;

[0024] 2. Intake duct; 21. Intake port; 211. Connecting section; 22. Exit section; 23. Exit port; 231. Seat ring; 232.

[0025] Rounded corner 3;

[0026] Air intake system 10. Detailed Implementation

[0027] Embodiments of the present invention are described in detail below, examples of which are illustrated in the accompanying drawings, wherein the same or similar reference numerals denote the same or similar elements or elements having the same or similar functions throughout. The embodiments described below with reference to the accompanying drawings are exemplary and intended to explain the present invention, and should not be construed as limiting the present invention.

[0028] In the description of this invention, it should be understood that the terms "length", "width", "upper", "lower", "inner", "outer", etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the drawings, and are only for the convenience of describing this invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of this invention.

[0029] Furthermore, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of this invention, "a plurality of" means at least two, such as two, three, etc., unless otherwise explicitly specified.

[0030] In this invention, unless otherwise explicitly specified and limited, the terms "installation," "connection," "linking," and "fixing," etc., should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral part; they can refer to a mechanical connection, an electrical connection, or a connection that allows communication between them; they can refer to a direct connection or an indirect connection through an intermediate medium; they can refer to the internal communication of two components or the interaction between two components. Those skilled in the art can understand the specific meaning of the above terms in this invention according to the specific circumstances.

[0031] The following is combined Figure 1 and Figure 2 The intake system 10 and the engine having the same are described in detail according to embodiments of the present invention.

[0032] Reference Figure 1 and Figure 2 As shown, the intake system 10 according to an embodiment of the present invention is used in an engine. The intake system 10 has a pressure stabilizing chamber 1 and an intake duct 2. The intake duct 2 includes an intake section 21, a connecting section 22, and an exhaust section 23. The connecting section 22 connects the intake section 21 and the exhaust section 23. The intake section 21 has an intake port 211 at one end away from the connecting section 22. The intake port 211 communicates with the pressure stabilizing chamber 1. In the direction from the connecting section 22 to the pressure stabilizing chamber 1, the flow area of ​​the intake section 21 gradually increases, and the exhaust section... The end of section 23 away from connecting section 22 has an outlet 231, which is adapted to communicate with the cylinder of the engine. On the orthographic projection plane of the intake system 10, the extension line of the center line of the intake section 21 and the extension line of the center line of the outlet section 23 intersect at point A. Point A is located within the orthographic projection of connecting section 22, and the center lines of the intake section 21 and the outlet section 23 are both located below point A. The intake system 10 can increase the intake flow rate and also increase the tumble intensity.

[0033] It is understandable that in the direction from the connecting section 22 to the pressure stabilizing chamber 1, the flow area of ​​the intake section 21 gradually increases. The intake section 21 can be funnel-shaped, which helps to reduce the flow resistance of gas from the pressure stabilizing chamber 1 to the intake section 21, and can significantly improve the gas flow coefficient, thereby helping to increase the gas flow rate from the pressure stabilizing chamber 1 into the intake passage 2, and further helping to increase the intake flow rate of the cylinder.

[0034] The centerlines of both the intake section 21 and the outlet section 23 are located below point A. The connecting section 22 forms a downward-curved structure. When the gas in the intake section 21 flows towards the outlet section 23, the gas can pass through the downward-curved connecting section 22. Under the action of inertia, the gas is deflected and flows towards the upper space of the outlet section 23. This part of the gas, together with the gas in the upper space of the outlet section 23, flows through the upper space of the outlet port 231, which can increase the gas velocity in the upper space of the outlet section 23. This is beneficial to increasing the gas flow rate entering the cylinder from the upper space of the outlet port 231, thereby improving the tumble intensity and facilitating the full mixing of fuel and gas in the cylinder. At the same time, in the direction from the pressure stabilizing chamber 1 towards the connecting section 22, the flow area of ​​the intake section 21 gradually decreases. When the gas flows from the intake section 21 to the connecting section 22, the gas velocity increases, which facilitates the gas flow towards the upper space of the outlet section 23 when passing through the connecting section 22, thereby further improving the tumble intensity.

[0035] In addition, the downward curvature of the intake section 21 relative to the connecting section 22 helps to reduce the overall height of the intake system 10, thereby reducing the space occupied by the intake system 10. The pressure stabilizing chamber 1 and the intake duct 2 are integrated into one unit, which helps to improve the compactness of the intake system 10. Furthermore, there is no need to use a manifold for transition between the pressure stabilizing chamber 1 and the intake duct 2, which helps to further reduce flow resistance and improve the flow coefficient.

[0036] According to the air intake system 10 of the present invention, the air intake duct 2 and the pressure regulating chamber 1 are integrated into one unit. The air intake duct 2 includes an air intake section 21, a connecting section 22 and an air outlet section 23. In the direction from the connecting section 22 to the pressure regulating chamber 1, the flow area of ​​the air intake section 21 gradually increases, which is beneficial to increasing the gas flow rate from the pressure regulating chamber 1 into the air intake duct 2, thereby increasing the air intake flow rate of the cylinder. The connecting section 22 is constructed with a downward bend, so that when the gas flows through the connecting section 22, it can flow into the upper space of the air outlet section 23, thereby increasing the gas flow rate entering the cylinder from the upper space of the air outlet 231, thereby improving the tumble intensity.

[0037] In some embodiments of the present invention, reference is made to... Figure 1 As shown, on the orthographic projection plane of the intake system 10, the angle formed by the extension of the centerline of the intake section 21 and the extension of the centerline of the exhaust section 23 is α and satisfies the relationship: 130°≤α≤170°. For example, α can be 130°, 150°, 170°, etc., so that the connecting section 22 is constructed as a large-angle structure, which can effectively reduce the flow resistance of the gas.

[0038] It is understandable that if α < 130°, the curvature of the connecting section 22 is large. When the gas flows from the inlet section 21 to the outlet section 23, the gas can flow through the large curvature connecting section 22. Under the action of inertia, the gas is difficult to turn, the flow resistance of the gas is large, resulting in a decrease in gas velocity and a low gas flow rate.

[0039] If α > 170°, the curvature of the connecting section 22 is small and the bending angle effect is poor. That is, when the gas flows through the connecting section 22, it is difficult for the gas to flow to the upper space of the outlet section 23, which is not conducive to improving the tumble flow intensity.

[0040] Within the range of 130° to 170°, the curvature of connecting section 22 is moderate and relatively gentle. Connecting section 22 is constructed with a large bend angle. When gas flows from intake section 21 to outlet section 23, the gas can flow into the upper space of outlet section 23 through the large bend angle of connecting section 22. This helps to increase the gas flow rate entering the cylinder from the upper space of outlet 231, effectively improving the tumble intensity and facilitating thorough mixing of fuel and gas in the cylinder. Simultaneously, the gas is easy to deflect, resulting in low flow resistance, which helps to reduce flow losses caused by gas separation.

[0041] In some embodiments of the present invention, reference is made to... Figure 1 As shown, the distance between point A and the center line of the cylinder is L1 and satisfies the relationship: 40mm≤L1≤60mm. For example, L1 can be 40mm, 50mm, 60mm, etc., which is beneficial to improve the bending angle effect, and thus to improve the tumble intensity, so as to facilitate the full mixing of fuel and gas in the cylinder.

[0042] It is understandable that when L1 < 40mm, the distance between point A and the center line of the cylinder is small, the length of the outlet section 23 is small, and after the gas flows into the outlet section 23 from the connecting section 22, the flow direction of the gas is not adjusted in time and flows directly into the cylinder of the engine through the outlet section 23, which is not conducive to improving the tumble intensity.

[0043] When L1 > 60mm, the distance between point A and the center line of the cylinder is large, and the length of the outlet section 23 is large. After the gas flows into the outlet section 23 from the connecting section 22, the gas can gradually become more evenly distributed when flowing in the outlet section 23. That is to say, the gas in the upper space of the outlet section 23 gradually mixes with the gas in the lower space of the outlet section 23, causing the gas flow velocity in the upper space of the outlet section 23 to gradually become consistent with the gas flow velocity in the lower space of the outlet section 23, which is not conducive to improving the tumble intensity.

[0044] Preferably, L1 is in the range of 40mm to 60mm, the distance between point A and the center line of the cylinder is moderate, the length of the outlet section 23 is moderate, and the gas in the inlet section 21 flows to the upper space of the outlet section 23 through the connecting section 22, which can accelerate the gas flow rate in the upper space of the outlet section 23. The high-speed gas in the upper space of the outlet section 23 can flow into the cylinder along the upper wall of the outlet section 23. The bending angle effect is good, which can effectively improve the tumbling intensity of the gas.

[0045] In some embodiments of the present invention, reference is made to... Figure 1 As shown, the distance between point A and the air inlet 211 is L2 and satisfies the relationship: 35mm ≤ L2 ≤ 55mm. For example, L2 can be 35mm, 45mm, 55mm, etc., so that the gas is fully rectified by the near-air section before flowing through the connecting section 22, thereby further improving the tumble flow intensity. Here, L2 is the radius R of the circle with point A as the center and tangent to the plane where the air inlet 211 is located. When the value of α changes, the distance between point A and the air inlet 211 can be kept constant.

[0046] It is understandable that when L2 < 35mm, the distance between point A and the air inlet 211 is small, the length of the air inlet section 21 is small, the time for the gas to flow from the air inlet section 21 to the connecting section 22 is short, the air inlet section 21 has a poor rectification effect on the gas flowing through it, the characteristic that the gas can flow along the axis of the connecting section 22 is not obvious, and the gas is difficult to flow to the upper space of the air outlet section 23, which is not conducive to improving the tumble intensity.

[0047] When L2 > 55 mm, the distance between point A and the air inlet 211 is large, the length of the air inlet section 21 is large, the flow time of the gas in the air inlet section 21 is long, the flow velocity of the gas is greatly reduced, which is not conducive to improving the tumble intensity.

[0048] Preferably, L2 is within the range of 35mm to 55mm, the distance between point A and the air inlet 211 is moderate, the length of the air inlet section 21 is moderate, and when the gas flows from the air inlet section 21 to the connecting section 22, the gas can be fully rectified in the air inlet section 21 before flowing into the connecting section 22, so that the gas moves along the axis of the air inlet section 21. When the gas flows through the connecting section 22, the gas can continue to move along the axis of the air inlet section 21 under the action of inertia and flow to the upper space of the air outlet section 23, which is conducive to improving the tumble intensity.

[0049] In some embodiments of the present invention, reference is made to... Figure 1 As shown, on the orthographic projection plane of the intake system 10, the angle formed by the centerline of the exhaust section 23 and the centerline of the cylinder is β and satisfies the relationship: 45°≤β≤50°. For example, β can be 45°, 47°, 50°, etc., so that the gas in the exhaust section 23 enters the engine at a certain incident angle, so that the gas can form tumble in the engine, which is beneficial to the full mixing of fuel and gas in the cylinder.

[0050] It is understandable that when β < 45°, the angle between the centerline of the exhaust section 23 and the centerline of the cylinder is small. When the gas flows into the cylinder along the centerline of the exhaust section 23, the incident angle of the gas is small, which is not conducive to the formation of tumble flow.

[0051] When β > 50°, the angle between the centerline of the exhaust section 23 and the centerline of the cylinder is large, the exhaust passage is relatively flat, the flow cross section of the exhaust section 23 is small, resulting in a low gas flow rate from the exhaust section 23 to the cylinder.

[0052] Preferably, β is in the range of 45° to 50°, and the angle formed by the centerline of the outlet section 23 and the centerline of the cylinder is moderate. When the gas flows into the cylinder along the centerline of the outlet section 23, the incident angle of the gas is moderate, which is conducive to improving the tumble intensity. At the same time, the flow cross section of the outlet section 23 is large, which is conducive to increasing the gas flow rate from the outlet section 23 to the cylinder.

[0053] In some embodiments of the present invention, reference is made to... Figure 1 As shown, the lower wall surface adjacent to the vent section 23 and the vent port 231 is a plane. During the casting process, when the core moves along the centerline of the vent section 23 and its position deviates, the angle between the lower wall surface adjacent to the vent section 23 and the vent port 231 and the axis of the cylinder remains unchanged. This ensures that the incident angle of the gas entering the cylinder from the vent section 23 is consistent, thus effectively solving the problem of poor performance consistency of the vent section 23 caused by the core position deviation. The lower wall surface adjacent to the vent section 23 and the vent port 231 can be a plane with a length of 10mm and a width of 5mm.

[0054] In some embodiments of the present invention, reference is made to... Figure 1 As shown, the angle between the lower wall surface of the air outlet section 23 adjacent to the air outlet 231 and the plane where the air outlet 231 is located is γ and satisfies the relationship: 25°≤γ≤30°, which is beneficial to improving the tumble flow intensity.

[0055] It is understandable that when γ < 25°, the incident angle of the gas is relatively large, which is not conducive to the formation of tumble flow.

[0056] When γ > 30°, when the gas in the lower space of the outlet section 23 flows into the cylinder along the lower wall of the outlet section 23, the flow direction of the gas in the lower space of the outlet section 23 is opposite to the direction of the tumble flow, resulting in a weakening of the tumble flow intensity.

[0057] Preferably, when γ is in the range of 25° to 30°, when the gas in the lower space of the outlet section 23 flows into the cylinder along the lower wall of the outlet section 23, the gas in the lower space of the outlet section 23 can flow to the upper part of the inlet 211 under the action of inertia, and flow into the cylinder together with the gas in the upper space of the outlet section 23, which is conducive to further improving the tumble intensity.

[0058] Reference Figure 1 As shown, a seat ring 232 is formed at the end of the air outlet section 23 near the cylinder. The seat ring 232 defines the air outlet 231 and is suitable for connecting to the cylinder.

[0059] In some embodiments of the present invention, reference is made to... Figure 1 and Figure 2 As shown, the angle between the upper wall of the intake section 21 and the plane where the intake port 211 is located is δ and satisfies the relationship: 84°≤δ≤86°. The angle between the lower wall of the intake section 21 and the plane where the intake port 211 is located is ε and satisfies the relationship: 54°≤ε≤56°. For example, δ can be 84°, 85°, 86°, etc., and ε can be 54°, 55°, 56°, etc., which helps to reduce the manufacturing difficulty of the intake system 10.

[0060] It should be noted that the upper and lower walls of the intake section 21 can be connected to the pressure stabilizing chamber 1 through rounded corners 3. The center of the rounded corners 3 is located outside the intake system 10, so that the intake port 211 has a wide opening structure, which is beneficial to increase the flow area of ​​the intake port 211. At the same time, the gas in the pressure stabilizing chamber 1 flows smoothly into the intake section 21 at the rounded corners 3. The rounded corners 3 can reduce the resistance of the gas flowing from the pressure stabilizing chamber 1 to the intake section 21 and increase the intake flow rate of the pressure stabilizing chamber 1 into the intake section 21.

[0061] It is understandable that when δ is in the range of 84° to 86°, the length of the fillet 3 connecting the upper wall of the intake section 21 to the pressure stabilizing cavity 1 can be reduced, and when ε is in the range of 54° to 56°, the length of the fillet 3 connecting the lower wall of the intake section 21 to the pressure stabilizing cavity 1 can be reduced. When there are multiple intake passages 2 in the intake system 10, interference between two adjacent intake passages 2 at the fillet 3 can be avoided, which helps to reduce the manufacturing difficulty of the intake system 10.

[0062] In some embodiments of the present invention, reference is made to... Figure 1 and Figure 2 As shown, the height of the air inlet 211 of the air intake section 21 is H1, and the width of the air inlet 211 is H2. The product of H1 and H2 is the size of the air inlet 211, that is, the effective flow area of ​​the air inlet 211.

[0063] In some embodiments of the present invention, reference is made to... Figure 2As shown, there are multiple intake ducts 2. Along the arrangement direction of the intake ducts 2, the flow area of ​​the pressure stabilizing chamber 1 gradually increases, and the side with the largest flow area of ​​the pressure stabilizing chamber 1 has the main intake inlet 11. That is to say, in the direction away from the main intake inlet 11, the flow area of ​​the pressure stabilizing chamber 1 gradually decreases. Gas can enter the pressure stabilizing chamber 1 through the main intake inlet 11, and the gas can move in the pressure stabilizing chamber 1 away from the main intake inlet 11. Since the flow area of ​​the pressure stabilizing chamber 1 gradually decreases, the gas flow velocity gradually increases, which can make the gas in the pressure stabilizing chamber 1 evenly distributed in the arrangement direction of the intake ducts 2, thereby facilitating the even distribution of gas flow into each intake duct 2. The main intake inlet 11 can be connected to the throttle valve.

[0064] In some embodiments of the present invention, reference is made to... Figure 2 As shown, the top view angle of the air intake 2 is η and satisfies the relationship: η≤10°. For example, η can be 8°, 9°, 10°, etc. To avoid the top view angle of the air intake 2 being too large, interference between two adjacent air intakes 2 can be effectively avoided. At the same time, in the direction from the air inlet 211 to the air outlet 231, the flow area of ​​the air intake 2 gradually decreases, which is conducive to increasing the gas flow rate and further improving the tumble intensity.

[0065] In some embodiments, refer to Figure 2 As shown, an intake duct 2 may include two outlet sections 23, a connecting section 22 and an intake section 21. Both outlet sections 23 are connected to the connecting section 22. The top view angle of the intake duct 2 is the angle formed by the mutually distant walls of the two outlet sections 23. Each outlet section 23 may be connected to its corresponding valve on the cylinder.

[0066] In some other embodiments, not shown in the figures, an intake duct 2 may include an exhaust section 23, a connecting section 22 and an intake section 21. The top view angle of the intake duct 2 is the angle formed by the upper and lower walls of the exhaust section 23. The exhaust section 23 may be connected to the valve on the cylinder.

[0067] According to another embodiment of the present invention, the engine includes a cylinder head having an intake system 10 as described above. The intake system 10 is integrated into the cylinder head, which is beneficial to improving the integration of the engine.

[0068] According to the air intake system 10 of the present invention, the air intake duct 2 and the pressure regulating chamber 1 are integrated into one unit. The air intake duct 2 includes an air intake section 21, a connecting section 22 and an air outlet section 23. In the direction from the connecting section 22 to the pressure regulating chamber 1, the flow area of ​​the air intake section 21 gradually increases, which is beneficial to increasing the gas flow rate from the pressure regulating chamber 1 into the air intake duct 2. The connecting section 22 is constructed with a downward bend, so that when the gas flows through the connecting section 22, it can flow into the upper space of the air outlet section 23, which is beneficial to increasing the gas flow rate from the upper space of the air outlet 231 into the cylinder, thereby improving the tumble intensity.

[0069] In the description of this specification, the references to terms such as "one embodiment," "some embodiments," "example," "specific example," or "some examples," etc., indicate that a specific feature, structure, material, or characteristic described in connection with that embodiment or example is included in at least one embodiment or example of the invention. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples. In addition, those skilled in the art can combine and integrate the different embodiments or examples described in this specification.

[0070] Although embodiments of the present invention have been shown and described above, it is understood that the above embodiments are exemplary and should not be construed as limiting the present invention. Those skilled in the art can make changes, modifications, substitutions and variations to the above embodiments within the scope of the present invention.

Claims

1. An intake system for an engine, characterized in that, The intake system (10) has a pressure stabilizing chamber (1) and an intake duct (2). The intake duct (2) includes an intake section (21), a connecting section (22) and an exhaust section (23). The connecting section (22) is connected between the intake section (21) and the exhaust section (23). The air intake section (21) has an air inlet (211) at one end away from the connecting section (22), and the air inlet (211) is connected to the pressure stabilizing chamber (1). In the direction from the connecting section (22) to the pressure stabilizing chamber (1), the flow area of ​​the air intake section (21) gradually increases. The exhaust section (23) has an exhaust port (231) at one end away from the connecting section (22), and the exhaust port (231) is adapted to communicate with the cylinder of the engine; On the orthographic projection plane of the intake system (10), the extension line of the center line of the intake section (21) and the extension line of the center line of the exhaust section (23) intersect at point A. Point A is located within the orthographic projection of the connecting section (22), and the center lines of the intake section (21) and the exhaust section (23) are both located below point A. On the orthographic projection plane of the intake system (10), the angle formed by the extension of the center line of the intake section (21) and the extension of the center line of the exhaust section (23) is α and satisfies the relationship: 130°≤α≤170°.

2. The intake system according to claim 1, characterized in that, The distance between point A and the center line of the cylinder is L1 and satisfies the relationship: 40mm≤L1≤60mm.

3. The intake system according to claim 1, characterized in that, The distance between point A and the air inlet (211) is L2 and satisfies the relationship: 35mm≤L2≤55mm.

4. The intake system according to any one of claims 2-3, characterized in that, On the orthographic projection plane of the intake system (10), the angle between the centerline of the exhaust section (23) and the centerline of the cylinder is β and satisfies the relationship: 45°≤β≤50°.

5. The intake system according to claim 4, characterized in that, The lower wall surface adjacent to the air outlet (23) and the air outlet (231) is a plane.

6. The intake system according to claim 5, characterized in that, The angle between the lower wall surface of the air outlet section (23) adjacent to the air outlet (231) and the plane where the air outlet (231) is located is γ and satisfies the relationship: 25°≤γ≤30°.

7. The intake system according to claim 1, characterized in that, The angle between the upper wall of the air intake section (21) and the plane where the air intake (211) is located is δ and satisfies the relationship: 84°≤δ≤86°; The angle between the lower wall of the air intake section (21) and the plane where the air intake (211) is located is ε and satisfies the relationship: 54°≤ε≤56°.

8. The intake system according to claim 1, characterized in that, There are multiple air intakes (2). Along the arrangement direction of the air intakes (2), the flow area of ​​the pressure stabilizing chamber (1) gradually increases, and the side with the largest flow area of ​​the pressure stabilizing chamber (1) has a total air intake inlet (11).

9. The intake system according to claim 8, characterized in that, The top-view angle of the air intake (2) is η and satisfies the relationship: η≤10°.

10. An engine, characterized in that, The engine includes a cylinder head having an intake system (10) according to any one of claims 1-9.

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