Engine piston, engine and vehicle

Abstract

The utility model discloses an engine piston, an engine and a vehicle, the engine piston comprises a piston body, along a first direction, two sides of the piston body are divided into an air inlet side and an air outlet side; the top face of the piston body is provided with a concave part, the distance between the center point of the concave part and the air inlet side is larger than that between the center point of the concave part and the air outlet side, the wall face of the concave part is an arc face, the maximum depth of the concave part is A, and the relation that A is larger than or equal to 4 mm and smaller than or equal to 8 mm is met. Therefore, the top face of the piston body is provided with the concave part, the distance between the center point of the concave part and the air inlet side is larger than the distance between the center point of the concave part and the air outlet side, the depth A of the concave part meets the relational expression that A is larger than or equal to 4 mm and smaller than or equal to 8 mm, airflow can form rotating tumble flow along the concave part and is rolled upwards, and therefore layering of mixed gas is achieved; a dense mixed gas area is formed near the spark plug, so that the combustion efficiency of the engine can be improved, the emission of the engine can be reduced, and the working performance of the engine can be improved.

Description

Technical Field

[0001] This utility model relates to the field of engines, and in particular to an engine piston, an engine, and a vehicle. Background Technology

[0002] In related technologies, an unreasonable design of the engine piston structure makes it impossible to form a reasonable air-fuel mixture stratification in the cylinder, resulting in low engine combustion efficiency, high emissions, and affecting engine performance. Utility Model Content

[0003] The present invention aims to at least solve one of the technical problems existing in the prior art. Therefore, one objective of the present invention is to provide an engine piston that can improve engine combustion efficiency, reduce emissions, and thus improve engine performance.

[0004] This utility model further proposes an engine.

[0005] This utility model further proposes a vehicle.

[0006] The engine piston according to this utility model includes: a piston body, which is divided into an intake side and an exhaust side along a first direction; the top surface of the piston body has a recessed portion, the distance between the center point of the recessed portion and the intake side is greater than the distance between the center point of the recessed portion and the exhaust side, the wall surface of the recessed portion is an arc surface and the maximum depth of the recessed portion is A, satisfying the relationship: 4mm≤A≤8mm.

[0007] According to the present invention, the engine piston has a recessed portion on the top surface of the piston body, and the distance between the center point of the recessed portion and the intake side is greater than the distance between the center point of the recessed portion and the exhaust side. The depth A of the recessed portion satisfies the relationship: 4mm≤A≤8mm. This allows the airflow to form a rotating tumble along the recessed portion and roll upwards, thereby achieving air-fuel mixture stratification and forming a rich air-fuel mixture zone near the spark plug. This improves the combustion efficiency of the engine and reduces the engine emissions, which is beneficial to improving the engine's performance.

[0008] In some examples of this utility model, the wall surface of the recess includes a first sub-wall surface and a second sub-wall surface, the second sub-wall surface is located on the side of the first sub-wall surface near the exhaust side and is connected to the first sub-wall surface, and the curvature of the first sub-wall surface is greater than the curvature of the second sub-wall surface.

[0009] In some examples of this utility model, along the first direction, the distance between the center point of the recess and the center section of the piston body along the second direction is B, which satisfies the relationship: 2mm≤B≤6mm, and the second direction is perpendicular to the first direction.

[0010] In some examples of this utility model, along the first direction, the distance between the contour of the recess facing the air intake side and the center section of the piston body along the second direction is C, which satisfies the relationship: 0mm<C≤1 / 4D, where D is the diameter of the piston body, and the second direction is perpendicular to the first direction.

[0011] In some examples of this utility model, along the first direction, the distance between the contour of the recess facing the intake side and the outer contour of the cylinder head combustion chamber of the piston body on the intake side is E, which satisfies the relationship: 10mm≤E≤20mm.

[0012] In some examples of this utility model, the top surface of the piston body has a protrusion, and the protrusion height of the protrusion is F, which satisfies the relationship: 1mm≤F≤4mm.

[0013] In some examples of this utility model, the contour of the recess includes a plurality of sequentially connected arc segments, all of which protrude toward the outer side of the piston body, and at least two of the arc segments have different curvatures.

[0014] In some examples of this utility model, the contour of the recess is symmetrically arranged along the central cross section of the piston body in the first direction.

[0015] The engine according to this utility model includes: a fuel injector, a spark plug, and an engine piston. The engine piston is the aforementioned engine piston. The angle between the central axis of the fuel injector and the central axis of the engine piston is α, satisfying the relationship: 0 degrees ≤ α ≤ 10 degrees. The angle between the central axis of the spark plug and the central axis of the engine piston is β, satisfying the relationship: 0 degrees ≤ β ≤ 10 degrees. The distance between the cathode of the spark plug and the central axis of the engine piston is G, satisfying the relationship: 0 mm < G ≤ 10 mm.

[0016] The vehicle according to this utility model includes the engine described above.

[0017] Additional aspects and advantages of this 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

[0018] The above and / or additional aspects and advantages of this utility model will become apparent and readily understood from the description of the embodiments taken in conjunction with the following drawings, in which:

[0019] Figure 1 and Figure 2 This is a cross-sectional view of the engine piston according to an embodiment of the present invention;

[0020] Figure 3 This is a top view of the engine piston according to an embodiment of the present utility model;

[0021] Figure 4 This is a schematic diagram of the cooperation between the engine piston and the engine according to an embodiment of the present invention.

[0022] Figure label:

[0023] Engine piston 100; Engine 99; Intake manifold 98; Cylinder 97;

[0024] Piston body 10; intake side 11; exhaust side 12; recess 13; first sub-wall 131; second sub-wall 132; arc segment 133; protrusion 14; central axis of fuel injector 15; central axis of spark plug 16; central axis of engine piston 17; outer contour of cylinder head combustion chamber intake side 18; central section of piston body along second direction 19; cathode of spark plug 20. Detailed Implementation

[0025] The embodiments of this utility model are described in detail below. Examples of these embodiments are shown 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 are only used to explain this utility model, and should not be construed as limiting this utility model.

[0026] The following is for reference. Figures 1-4 Description of an engine piston 100 according to an embodiment of the present invention.

[0027] like Figures 1-4 As shown, the engine piston 100 according to an embodiment of the present utility model includes: piston body 10.

[0028] Along the first direction (i.e.) Figure 3 (As shown in the Z direction), the piston body 10 is divided into an intake side 11 and an exhaust side 12 on both sides; the top surface of the piston body 10 has a recess 13, the distance between the center point of the recess 13 and the intake side 11 is greater than the distance between the center point of the recess 13 and the exhaust side 12, the wall of the recess 13 is an arc surface and the maximum depth of the recess 13 is A, satisfying the relationship: 4mm≤A≤8mm.

[0029] The engine piston 100 of this application can be used in, but is not limited to, gasoline engines, diesel engines, hydrogen internal combustion engines, etc. This application will use the application of the engine piston 100 in a hydrogen internal combustion engine as an example for illustration.

[0030] Among them, along the first direction (i.e. Figure 3 (As shown in the Z direction), the piston body 10 has two opposite sides, one side being the intake side 11 and the other side being the exhaust side 12. The piston body 10 has a recess 13, which is located on the top surface of the piston body 10. The recess 13 has a center point, and the distance between the center point of the recess 13 and the intake side 11 is greater than the distance between the center point of the recess 13 and the exhaust side 12. In other words, the center point of the recess 13 is closer to the exhaust side 12 of the piston body 10.

[0031] The wall surface of the recess 13 is curved, and the maximum depth of the recess 13 is A, which satisfies the relationship: 4mm ≤ A ≤ 8mm. That is, the distance A between the lowest point of the recess 13 and the top surface of the piston body 10 satisfies the relationship 4mm ≤ A ≤ 8mm. The maximum depth A of the recess 13 can be any value between 4mm and 8mm. For example, the maximum depth A of the recess 13 can be, but is not limited to, 4mm, 6mm, 8mm, etc. As some embodiments of this application, the maximum depth A of the recess 13 is 6mm.

[0032] As some embodiments of this application, the engine piston 100 of this application is applied to the engine 99 of a hydrogen internal combustion engine, the engine 99 also including a spark plug and a fuel injector.

[0033] It should be noted that, as Figure 4 As shown, during the intake stroke of engine 99, the engine piston 100 moves downward, and fresh air enters the cylinder 97 of engine 99 through the intake port 98. The recess 13 enables the airflow to form a large-scale clockwise rotating tumble along the walls of cylinder 97 and piston body 10. This tumble motion generates strong turbulence in the air within cylinder 97, which promotes thorough mixing of air and hydrogen. During the compression stroke of engine 99, as piston body 10 moves upward, the internal volume of cylinder 97 decreases, the large-scale tumble gradually decreases, and the tumble is compressed, causing the air-fuel mixture to form a rich zone near the spark plug. This accelerates flame propagation speed, optimizes combustion stability, contributes to the ignition stability of engine 99, reduces engine emissions, and improves engine performance.

[0034] Furthermore, it should be explained that the maximum depth A of the recess 13 affects the rich mixture zone formed near the spark plug. If the maximum depth of the recess 13 is too shallow, the mixture will be lifted too low, thus failing to form a rich mixture zone near the spark plug and preventing mixture stratification. If the maximum depth of the recess 13 is too deep, the mixture will be lifted too high, again failing to form a rich mixture zone near the spark plug and preventing mixture stratification. By setting the maximum depth A of the recess 13 to any value between 4mm and 8mm, the maximum depth of the recess 13 can be reasonably set, allowing the mixture to form a rich mixture zone near the spark plug, which is beneficial for forming a more ideal combustion process. Moreover, if the maximum depth of the recess 13 is too deep, it will also affect the structural strength of the piston body 10. By setting the maximum depth A of the recess 13 to any value between 4mm and 8mm, the structural strength of the piston body 10 can be increased, which is beneficial for improving the reliability of the piston body 10.

[0035] Therefore, by making the top surface of the piston body 10 have a recess 13, and making the distance between the center point of the recess 13 and the intake side 11 greater than the distance between the center point of the recess 13 and the exhaust side 12, and making the depth A of the recess 13 satisfy the relationship: 4mm≤A≤8mm, the airflow can form a rotating tumble along the recess 13 and roll upward to achieve mixture stratification, forming a rich mixture zone near the spark plug, thereby improving the combustion efficiency of the engine 99 and reducing the emissions of the engine 99, which is beneficial to improving the working performance of the engine 99.

[0036] In some embodiments of this utility model, such as Figure 2 and Figure 3 As shown, the wall surface of the recess 13 includes a first sub-wall surface 131 and a second sub-wall surface 132. The second sub-wall surface 132 is located on the side of the first sub-wall surface 131 near the exhaust side 12 and is connected to the first sub-wall surface 131. The curvature of the first sub-wall surface 131 is greater than the curvature of the second sub-wall surface 132.

[0037] The first sub-wall 131 has a side closer to the exhaust side 12 and a side farther from the exhaust side 12. The second sub-wall 132 is located on the side of the first sub-wall 131 closer to the exhaust side 12, meaning the second sub-wall 132 is closer to the exhaust side 12. The second sub-wall 132 is connected to the first sub-wall 131. The curvature of the first sub-wall 131 is greater than that of the second sub-wall 132, meaning the first sub-wall 131 has a greater degree of curvature compared to the second sub-wall 132.

[0038] By making the curvature of the first sub-wall 131 greater than that of the second sub-wall 132, it is easier to form a large-scale tumble flow in the cylinder 97, thereby promoting the full mixing of air and hydrogen. Furthermore, the size of the tumble flow can be controlled, which helps to guide the mixture to roll up at a suitable height and move towards the spark plug, ensuring the formation of a rich mixture zone near the spark plug, improving combustion efficiency, reducing emissions, and improving the performance of the engine 99.

[0039] In some embodiments of this utility model, such as Figure 3 As shown, along the first direction (i.e. Figure 3 As shown in the Z direction), the center point of the recess 13 is along the second direction (i.e., the piston body). Figure 3 The distance between the center sections 19 in the X direction (as shown) is B, satisfying the relationship: 2mm ≤ B ≤ 6mm, and the distance in the second direction (i.e. Figure 3 The X direction shown) and the first direction (i.e. Figure 3 (The Z direction shown is perpendicular.)

[0040] The center point of the recess 13 is aligned with the piston body along the second direction (i.e., Figure 3 The distance B between the center section 19 (shown in the X direction) and the piston body along the second direction (i.e., the distance B satisfies the relationship: 2mm ≤ B ≤ 6mm, that is, the center point of the recess 13 and the piston body along the second direction (i.e., the distance B between the center section 19 and the piston body along the second direction) satisfy the relationship: 2mm ≤ B ≤ 6mm. Figure 3 The spacing B between the center sections 19 (shown in the X direction) can be any value between 2 mm and 6 mm. For example, the center point of the recess 13 and the piston body along the second direction (i.e., Figure 3 The distance B between the center sections 19 (shown in the X direction) can be, but is not limited to, 2mm, 4mm, 6mm, etc. As some embodiments of this application, the center point of the recess 13 and the piston body along the second direction (i.e., Figure 3 The spacing between the central sections 19 (shown in the X direction) is 4 mm.

[0041] By aligning the center point of the recess 13 with the piston body along the second direction (i.e.) Figure 3 The spacing B between the central sections 19 (shown in the X direction) can be any value between 2mm and 6mm, which can make the position of the center point of the recess 13 reasonable, which is conducive to the formation of a rich zone of the mixture near the spark plug and the formation of tumble flow in the cylinder 97, thereby enabling the air and hydrogen to be fully mixed to improve the combustion efficiency of the engine 99.

[0042] In some embodiments of this utility model, such as Figure 3 As shown, along the first direction (i.e. Figure 3 As shown in the Z direction), the contour of the recessed portion 13 toward the intake side 11 is parallel to the piston body along the second direction (i.e., Figure 3The distance between the center sections 19 (shown in the X direction) is C, satisfying the relationship: 0mm < C ≤ 1 / 4D, where D is the diameter of the piston body 10, and the distance in the second direction (i.e., Figure 3 The X direction shown) and the first direction (i.e. Figure 3 (The Z direction shown is perpendicular.)

[0043] Where D is the diameter of the piston body 10, that is, along the first direction (i.e. Figure 3 As shown in the Z direction), the contour of the recessed portion 13 toward the intake side 11 is parallel to the piston body along the second direction (i.e., Figure 3 The distance C between the center sections 19 (shown in the X direction) is greater than 0 mm and less than or equal to one-quarter of the diameter of the piston body 10. The contour of the recess 13 facing the intake side 11 is parallel to the piston body along the second direction (i.e., Figure 3 The spacing C between the center sections 19 (shown in the X direction) can be any value between 0 and one-quarter of the diameter of the piston body 10, and the second direction (i.e. Figure 3 The X direction shown) and the first direction (i.e. Figure 3 The Z-direction shown is perpendicular to each other.

[0044] It should be noted that the contour of the recessed portion 13 facing the intake side 11 is parallel to that of the piston body 10 along the second direction (i.e., Figure 3 The spacing C between the central sections 19 (shown in the X direction) directly affects the formation of the air-fuel mixture. If the spacing C is too short, the airflow will rise prematurely, resulting in the air-fuel mixture failing to form a rich zone near the spark plug at the ignition point. If the spacing C is too long, the airflow will rise late, resulting in the air-fuel mixture failing to form a rich zone near the spark plug at the ignition point.

[0045] By aligning the contour of the recess 13 toward the intake side 11 with the piston body 10 along the second direction (i.e. Figure 3 The distance C between the center sections 19 (shown in the X direction) is greater than 0 mm and less than or equal to one-quarter of the diameter of the piston body 10, which enables the air-fuel mixture to rise at the appropriate time, which is beneficial to form a rich zone of air-fuel mixture near the spark plug at the moment of ignition, significantly improving the stratification effect and thus improving the combustion efficiency of the engine 99.

[0046] In some embodiments of this utility model, such as Figure 3 As shown, along the first direction (i.e. Figure 3 (As shown in the Z direction), the distance between the contour of the recessed part 13 facing the intake side 11 and the outer contour 18 of the cylinder head combustion chamber of the piston body 10 on the intake side is E, which satisfies the relationship: 10mm≤E≤20mm.

[0047] Among them, along the first direction (i.e. Figure 3(As shown in the Z direction), the distance E between the contour of the recessed portion 13 facing the intake side 11 and the outer contour 18 of the cylinder head combustion chamber of the piston body 10 on the intake side satisfies the relationship: 10mm≤E≤20mm. That is to say, the distance E between the contour of the recessed portion 13 facing the intake side 11 and the outer contour 18 of the cylinder head combustion chamber of the piston body 10 on the intake side can be any value between 10mm and 20mm. For example, the distance E between the contour of the recessed portion 13 facing the intake side 11 and the outer contour 18 of the cylinder head combustion chamber of the piston body 10 on the intake side can be, but is not limited to, 10mm, 15mm, 20mm, etc. As some embodiments of this application, the distance E between the contour of the recessed portion 13 facing the intake side 11 and the outer contour 18 of the cylinder head combustion chamber of the piston body 10 on the intake side is 15mm.

[0048] By making the distance E between the contour of the recess 13 facing the intake side 11 and the outer contour 18 of the cylinder head combustion chamber of the piston body 10 on the intake side any value between 10mm and 20mm, the direction of the airflow of the air-fuel mixture can be guided, and the formation of tumble can be promoted so that the air-fuel mixture forms a rich zone near the spark plug and a lean zone in other positions, thereby stratifying the air-fuel mixture concentration, which is beneficial to improving the combustion efficiency of the engine 99.

[0049] In some embodiments of this utility model, such as Figure 1 As shown, the top surface of the piston body 10 has a protrusion 14, and the protrusion height of the protrusion 14 is F, which satisfies the relationship: 1mm≤F≤4mm.

[0050] The protrusion height F of the protrusion 14 satisfies the relationship 1mm≤F≤4mm. That is, the protrusion height F of the protrusion 14 can be any value between 1mm and 4mm. For example, the protrusion height F of the protrusion 14 can be, but is not limited to, 1mm, 2.5mm, 4mm, etc. As some embodiments of this application, the protrusion height F of the protrusion 14 is 3mm.

[0051] By making the top surface of the piston body 10 have a protrusion 14, and making the protrusion height F of the protrusion 14 any value between 1mm and 4mm, the protrusion height F of the protrusion 14 can be reasonable. During the compression process, the air-fuel mixture can be concentrated near the spark plug to form a rich zone, while other positions form a lean zone, thus improving the stratification effect.

[0052] In some embodiments of this utility model, such as Figure 3 As shown, the contour of the recess 13 includes a plurality of sequentially connected arc segments 133, all of which protrude toward the outside of the piston body 10, and at least two arc segments 133 have different curvatures.

[0053] The number of arc segments 133 can be, but is not limited to, two, three, four, etc. As some embodiments of this application, the number of arc segments 133 is two, the two arc segments 133 are connected in sequence, both arc segments 133 protrude toward the outside of the piston body 10, and the curvature of the two arc segments 133 is different. As some embodiments of this application, the number of arc segments 133 is four, the four arc segments 133 are connected in sequence, all four arc segments 133 protrude toward the outside of the piston body 10, and at least two of the four arc segments 133 have different curvatures.

[0054] This configuration promotes airflow movement and mixing, allowing the airflow to rotate in a predetermined direction, laying a good foundation for the subsequent combustion process. Furthermore, this configuration enables the piston body 10 to maintain good structural integrity and strength when subjected to various complex loads, reducing the risk of failure such as cracks and damage to the piston body 10 due to stress concentration, and thus extending the service life of the piston body 10. In addition, this configuration can guide the airflow to effectively form a tumble flow.

[0055] In some embodiments of this utility model, such as Figure 3 As shown, along the piston body 10 in the first direction (i.e. Figure 3 The central cross section (shown in the Z direction) shows that the contour of the recess 13 is symmetrically arranged with respect to the piston body 10 along the first direction (i.e., Figure 3 The central cross section (shown in the Z direction) is symmetrical. This arrangement makes the structure of the recess 13 reasonable, allowing the airflow to form a stable tumble flow through the recess 13, promoting the full mixing of air and hydrogen. Furthermore, this arrangement reduces the manufacturing difficulty of the piston body 10 and helps improve the production efficiency of the piston body 10.

[0056] The engine 99 according to an embodiment of the present invention includes: a fuel injector, a spark plug, and an engine piston 100. The engine piston 100 is the same as described above. The angle between the central axis 15 of the fuel injector and the central axis 17 of the engine piston is α, satisfying the relationship: 0 degrees ≤ α ≤ 10 degrees. The angle between the central axis 16 of the spark plug and the central axis 17 of the engine piston is β, satisfying the relationship: 0 degrees ≤ β ≤ 10 degrees. The distance between the cathode 20 of the spark plug and the central axis 17 of the engine piston is G, satisfying the relationship: 0 mm < G ≤ 10 mm.

[0057] Among them, such as Figure 2As shown, the angle α between the central axis 15 of the fuel injector and the central axis 17 of the engine piston satisfies the relationship 0 degrees ≤ α ≤ 10 degrees. That is, the angle α between the central axis 15 of the fuel injector and the central axis 17 of the engine piston can be any value between 0 degrees and 10 degrees. For example, the angle α between the central axis 15 of the fuel injector and the central axis 17 of the engine piston can be, but is not limited to, 0 degrees, 5 degrees, 10 degrees, etc. As some embodiments of this application, the angle α between the central axis 15 of the fuel injector and the central axis 17 of the engine piston is 5 degrees.

[0058] like Figure 2 As shown, the angle β between the central axis 16 of the spark plug and the central axis 17 of the engine piston satisfies the relationship 0 degrees ≤ β ≤ 10 degrees. That is, the angle β between the central axis 16 of the spark plug and the central axis 17 of the engine piston can be any value between 0 degrees and 10 degrees. For example, the angle β between the central axis 16 of the spark plug and the central axis 17 of the engine piston can be, but is not limited to, 0 degrees, 5 degrees, 10 degrees, etc. As some embodiments of this application, the angle β between the central axis 16 of the spark plug and the central axis 17 of the engine piston is 5 degrees.

[0059] like Figure 2 As shown, the distance G between the spark plug cathode 20 and the central axis 17 of the engine piston satisfies the relationship 0mm < G ≤ 10mm. That is, the distance G between the spark plug cathode 20 and the central axis 17 of the engine piston can be any value between 0mm and 10mm. For example, the distance G between the spark plug cathode 20 and the central axis 17 of the engine piston can be, but is not limited to, 1mm, 5mm, 10mm, etc. As some embodiments of this application, the distance G between the spark plug cathode 20 and the central axis 17 of the engine piston is 5mm.

[0060] This configuration allows for a reasonable arrangement of the relative positions and angles of the fuel injector, spark plug, and engine piston 100. During compression, the fuel injector can precisely inject hydrogen fuel into the recess 13. As the piston body 10 moves upward, the hydrogen in the recess 13 rises along the wall of the recess 13 towards the intake side 11 and moves toward the spark plug. This allows the air-fuel mixture to form a rich zone near the spark plug, resulting in stratification of the air-fuel mixture in the cylinder 97 of the engine 99. This improves the combustion efficiency of the engine 99. Furthermore, this configuration enhances the ignition stability of the engine 99, which is beneficial for improving the reliability of the engine 99.

[0061] Furthermore, by making the top surface of the piston body 10 have a recess 13, and making the distance between the center point of the recess 13 and the intake side 11 greater than the distance between the center point of the recess 13 and the exhaust side 12, and making the depth A of the recess 13 satisfy the relationship: 4mm≤A≤8mm, the airflow can form a rotating tumble along the recess 13 and roll upwards to achieve mixture stratification, forming a rich mixture zone near the spark plug, thereby improving the combustion efficiency of the engine 99 and reducing the emissions of the engine 99, which is beneficial to improving the working performance of the engine 99.

[0062] The vehicle according to the present invention includes the engine 99 of the above embodiment. By having a recessed portion 13 on the top surface of the piston body 10, and making the distance between the center point of the recessed portion 13 and the intake side 11 greater than the distance between the center point of the recessed portion 13 and the exhaust side 12, and making the depth A of the recessed portion 13 satisfy the relationship: 4mm≤A≤8mm, the airflow can form a rotating tumble along the recessed portion 13 and roll upward to achieve air-fuel mixture stratification, forming a rich air-fuel mixture zone near the spark plug, thereby improving the combustion efficiency of the engine 99 and reducing the emissions of the engine 99, which is beneficial to improving the working performance of the engine 99.

[0063] In the description of this utility model, it should be understood that the terms "center", "longitudinal", "transverse", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", "axial", "radial", "circumferential", etc., indicating the orientation or positional relationship are based on the orientation or positional relationship shown in the accompanying drawings, and are only for the convenience of describing this utility model and simplifying the description, and are not intended to 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 utility model.

[0064] In the description of this utility model, "first feature" and "second feature" may include one or more of the features.

[0065] In the description of this utility model, "multiple" means two or more.

[0066] In the description of this utility model, the first feature being "above" or "below" the second feature may include the first and second features being in direct contact, or it may include the first and second features not being in direct contact but being in contact through another feature between them.

[0067] In the description of this utility model, the terms "above", "over" and "on top" for the first feature and the second feature include the first feature being directly above or diagonally above the second feature, or simply indicate that the first feature is at a higher horizontal level than the second feature.

[0068] In the description of this specification, the references to terms such as "one embodiment," "some embodiments," "illustrative embodiment," "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 present 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.

[0069] Although embodiments of the present invention have been shown and described, those skilled in the art will understand that various changes, modifications, substitutions and alterations can be made to these embodiments without departing from the principles and spirit of the present invention, the scope of which is defined by the claims and their equivalents.

Claims

1. An engine piston (100), characterized in that, include: The piston body (10) is divided into an intake side (11) and an exhaust side (12) on both sides along the first direction. The piston body (10) has a recess (13) on its top surface. The distance between the center point of the recess (13) and the intake side (11) is greater than the distance between the center point of the recess (13) and the exhaust side (12). The wall of the recess (13) is an arc surface and the maximum depth of the recess (13) is A, satisfying the relationship: 4mm≤A≤8mm.

2. The engine piston (100) according to claim 1, characterized in that, The wall surface of the recess (13) includes a first sub-wall surface (131) and a second sub-wall surface (132). The second sub-wall surface (132) is located on the side of the first sub-wall surface (131) near the exhaust side (12) and is connected to the first sub-wall surface (131). The curvature of the first sub-wall surface (131) is greater than the curvature of the second sub-wall surface (132).

3. The engine piston (100) according to claim 1, characterized in that, Along the first direction, the distance between the center point of the recess (13) and the center section (19) of the piston body along the second direction is B, which satisfies the relationship: 2mm≤B≤6mm, and the second direction is perpendicular to the first direction.

4. The engine piston (100) according to claim 1, characterized in that, Along the first direction, the distance between the contour of the recess (13) toward the air intake side (11) and the center section (19) of the piston body along the second direction is C, which satisfies the relationship: 0mm<C≤1 / 4D, where D is the diameter of the piston body (10), and the second direction is perpendicular to the first direction.

5. The engine piston (100) according to claim 1, characterized in that, Along the first direction, the distance between the contour of the recess (13) toward the intake side (11) and the outer contour (18) of the cylinder head combustion chamber of the piston body (10) on the intake side is E, which satisfies the relationship: 10mm≤E≤20mm.

6. The engine piston (100) according to claim 1, characterized in that, The piston body (10) has a protrusion (14) on its top surface. The protrusion height of the protrusion (14) is F, which satisfies the relationship: 1mm≤F≤4mm.

7. The engine piston (100) according to any one of claims 1-6, characterized in that, The contour of the recess (13) includes a plurality of sequentially connected arc segments (133), all of which protrude toward the outside of the piston body (10), and at least two of the arc segments (133) have different curvatures.

8. The engine piston (100) according to claim 7, characterized in that, Along the central cross section of the piston body (10) in the first direction, the contour of the recess (13) is symmetrically arranged.

9. An engine (99), characterized in that, include: The fuel injector, spark plug, and engine piston (100) are provided, wherein the engine piston (100) is the same as any one of claims 1-8, the angle between the central axis (15) of the fuel injector and the central axis (17) of the engine piston is α, satisfying the relationship: 0 degrees ≤ α ≤ 10 degrees; the angle between the central axis (16) of the spark plug and the central axis (17) of the engine piston is β, satisfying the relationship: 0 degrees ≤ β ≤ 10 degrees; the distance between the cathode (20) of the spark plug and the central axis (17) of the engine piston is G, satisfying the relationship: 0 mm < G ≤ 10 mm.

10. A vehicle, characterized in that, Includes the engine (99) according to claim 9.

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