Engine and vehicle

Abstract

The utility model discloses an engine and a vehicle, the engine comprises a cylinder, a movable piston is arranged in the cylinder, and a combustion chamber is defined between the piston and the cylinder; the middle ejector and the side ejector are both located at the top of the combustion chamber, and the distance between the middle ejector and the center of the top of the combustion chamber is smaller than the distance between the side ejector and the center of the top of the combustion chamber; wherein a concave area which is open towards the combustion chamber is formed on the top surface of the piston, and the middle injector and the side injector are suitable for injecting fuel towards the concave area respectively. According to the engine, the uniformity of mixed gas in the cylinder can be improved, the combustion speed can be increased, oil consumption can be reduced, the discharge amount of harmful substances can be reduced, meanwhile, the tumble intensity can be enhanced, and the turbulence energy can be improved.

Description

Technical Field

[0001] The utility model relates to the technical field of engines, in particular to an engine and a vehicle with the engine. Background Art

[0002] In the related art, the uniformity of the mixture in the cylinder is poor, the combustion speed is slow, the fuel consumption and the emission of harmful substances are high, and there is room for improvement. Utility Model Content

[0003] The present invention aims to solve at least one of the technical problems existing in the prior art. To this end, the present invention provides an engine that improves the uniformity of the mixture in the cylinder, accelerates combustion, reduces fuel consumption, and reduces the emission of harmful substances. At the same time, it can enhance the tumble flow intensity and increase turbulent kinetic energy.

[0004] According to an embodiment of the present invention, the engine includes: a cylinder, a movable piston is provided in the cylinder, and a combustion chamber is defined between the piston and the cylinder; a central injector and a side injector, the central injector and the side injector are both located at the top of the combustion chamber, and the distance between the central injector and the center of the top of the combustion chamber is smaller than the distance between the side injector and the center of the top of the combustion chamber; wherein a recessed area open toward the combustion chamber is formed on the top surface of the piston, and the central injector and the side injector are suitable for respectively injecting fuel toward the recessed areas.

[0005] According to the engine of the embodiment of the present invention, by arranging a central injector and a side injector to respectively inject fuel into the recessed area of ​​the piston, the uniformity of the mixture in the cylinder can be improved, the combustion speed can be accelerated, the fuel consumption can be reduced, and the emission of harmful substances can be reduced. At the same time, the tumble intensity can be enhanced and the turbulent kinetic energy can be improved.

[0006] According to some embodiments of the engine of the present invention, the recessed area is configured as a circular area, and the diameter of the recessed area is A1, and the depth of the recessed area is A2, and the following condition is satisfied: 10≤A1 / A2≤16.

[0007] According to the engine of some embodiments of the present invention, the injection range of the side injector is B1, the injection range of the center injector is B2, and the following relationship is satisfied: 1.2≤B1 / B2≤1.7.

[0008] According to the engine of some embodiments of the present invention, the top surface of the piston is further formed with an intake valve avoidance recess and an exhaust valve avoidance recess, and the intake valve avoidance recess and the exhaust valve avoidance recess are both spaced apart from the recess area.

[0009] According to some embodiments of the engine of the present invention, the distance from the recessed area to the intersection of the intake valve avoidance recess and the top surface of the piston is C1, and the distance from the recessed area to the intersection of the exhaust valve avoidance recess and the top surface of the piston is C2, and the following condition is satisfied: C1<C2.

[0010] According to some embodiments of the engine of the present invention, the recessed area is located in a central area of ​​the surface of the piston facing the combustion chamber.

[0011] According to the engine of some embodiments of the present invention, a spark plug is provided at the top of the combustion chamber above the recessed area, and the side injector is suitable for injecting fuel into an area with a diameter outside a set diameter centered on the electrode of the spark plug, and the side injector is suitable for injecting fuel into an area with a diameter within a set diameter centered on the electrode of the spark plug.

[0012] According to some embodiments of the engine of the present invention, the set diameter is D, and satisfies: 25mm≤D≤27mm.

[0013] According to some embodiments of the present invention, the electrode of the spark plug includes a first plate surface electrode and a second plate surface electrode relatively distributed in the up and down directions, an electrode gap is formed between the first plate surface electrode and the second plate surface electrode, the surface area of ​​the first plate surface electrode is E1, the surface area of ​​the second plate surface electrode is E2, and the following conditions are satisfied: 0.18≤E1 / E2≤0.3.

[0014] The utility model also provides a vehicle.

[0015] A vehicle according to an embodiment of the present invention includes the engine described in the above embodiment.

[0016] Additional aspects and advantages of the present invention will be given in part in the following description and will become apparent from the following description or learned through practice of the present invention. BRIEF DESCRIPTION OF THE DRAWINGS

[0017] The above and / or additional aspects and advantages of the present invention will become apparent and readily understood from the description of the embodiments in conjunction with the following drawings, in which:

[0018] Figure 1 It is a structural schematic diagram of an engine according to an embodiment of the present utility model;

[0019] Figure 2 is a cross-sectional view of an engine according to an embodiment of the present utility model;

[0020] Figure 3 Schematic diagram of radial flow of mixed gas in an engine according to an embodiment of the present utility model;

[0021] Figure 4 Schematic diagram of the axial flow of mixed gas in an engine according to an embodiment of the present utility model;

[0022] Figure 5 It is a structural schematic diagram of a piston according to an embodiment of the utility model.

[0023] Reference numerals:

[0024] Cylinder 1 , piston 2 , recessed area 21 , intake valve avoidance recess 22 , exhaust valve avoidance recess 23 , combustion chamber 31 , center injector 4 , side injector 5 , spark plug 6 , first plate surface electrode 61 , second plate surface electrode 62 . DETAILED DESCRIPTION

[0025] The following describes embodiments of the present invention in detail. Examples of the embodiments are shown in the accompanying drawings, wherein the same or similar reference numerals throughout represent the same or similar elements or elements having the same or similar functions. The embodiments described below with reference to the accompanying drawings are exemplary and are intended only to explain the present invention and are not to be construed as limiting the present invention.

[0026] In the description of the present invention, it should be understood that the terms "center", "longitudinal", "transverse", "length", "width", "thickness", "up", "down", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inside", "outside", "clockwise", "counterclockwise", "axial", "radial", "circumferential" and the like indicate orientations or positional relationships based on the orientations or positional relationships shown in the accompanying drawings. They are only for the convenience of describing the present invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be understood as a limitation on the present invention. In addition, features defined as "first" or "second" may explicitly or implicitly include one or more of such features. In the description of the present invention, unless otherwise specified, "multiple" means two or more.

[0027] In the description of this utility model, it should be noted that, unless otherwise expressly specified or limited, the terms "mounted," "connected," and "connected" should be understood in a broad sense. For example, they can refer to fixed connections, detachable connections, or integral connections; mechanical connections, electrical connections; direct connections, indirect connections through an intermediate medium, and internal communication between two components. Those skilled in the art will understand the specific meanings of the above terms in this utility model based on the specific circumstances.

[0028] Unless otherwise specified, the front-to-back direction in this application is the longitudinal direction of the vehicle, that is, the X direction; the left-right direction is the lateral direction of the vehicle, that is, the Y direction; and the up-down direction is the vertical direction of the vehicle, that is, the Z direction.

[0029] First of all, it should be noted that traditional engines are also equipped with central injectors and side injectors to inject oil in the compression stroke and intake stroke respectively to achieve uniform combustion in the cylinder. However, the piston, oil beam and gas flow arrangement in the existing technology are difficult to design and difficult to implement, and cannot achieve the effect of enhancing the tumble intensity and improving the turbulent kinetic energy.

[0030] The utility model provides an engine, which can improve the uniformity of mixed gas in a cylinder, accelerate the combustion speed, reduce fuel consumption, and at the same time, enhance the tumble flow intensity and improve the turbulent kinetic energy.

[0031] like Figure 1-Figure 5 As shown, an engine according to an embodiment of the present invention includes: a cylinder 1, a center injector 4 and a side injector 5.

[0032] The cylinder 1 is the main structure of the engine. Its interior is a cavity to form a storage space for accommodating the piston 2. A movable piston 2 is provided in the cylinder 1, that is, the piston 2 can reciprocate up and down in the storage space to compress the gas and provide power for the engine.

[0033] A closed combustion chamber 31 is defined between the top of the piston 2 and the top wall of the cylinder 1. Within this chamber, fuel mixes with air and burns to generate power. In practice, during the intake stroke—that is, as the piston 2 moves downward—air enters the combustion chamber 31 and mixes with the fuel to form a fuel-air mixture. The piston 2 continues its downward motion until it reaches bottom dead center (BDC) of the intake stroke. It then moves upward, compressing the fuel-air mixture within the cylinder 1. When the piston 2 reaches near top dead center, the high-temperature, high-pressure gas generated by the combustion of the fuel-air mixture continues to push the piston 2 downward, transmitting power to the crankshaft, which then rotates, thereby enabling engine operation.

[0034] The center injector 4 and the side injector 5 are both located at the top of the combustion chamber 31 , and the distance between the center injector 4 and the center of the top of the combustion chamber 31 is smaller than the distance between the side injector 5 and the center of the top of the combustion chamber 31 .

[0035] Specifically, the central injector 4 and the side injector 5 are both used to inject fuel into the combustion chamber 31. Figure 1As shown, the center injector 4 and the side injector 5 are both located at the top of the combustion chamber 31. The center injector 4 is arranged in the central area of ​​the combustion chamber 31 and injects fuel during the compression stroke so that the fuel can be directly injected into the center of the combustion chamber 31 and can be mixed with the air more quickly, thereby improving the combustion efficiency; the side injector 5 is arranged in the side area of ​​the combustion chamber 31 and injects fuel during the intake stroke so that the fuel can be sprayed from the side of the combustion chamber 31 to the center of the combustion chamber 31, further making the fuel and air mixed more evenly.

[0036] Therefore, the two injectors spray fuel separately in different strokes to achieve oil-gas mixing, which is conducive to better and more even mixing of oil and gas.

[0037] Furthermore, a recessed area 21 open toward the combustion chamber 31 is formed on the top surface of the piston 2 , and the center injector 4 and the side injector 5 are adapted to inject fuel toward the recessed area 21 , respectively.

[0038] Specifically, refer to the attached Figure 2 As shown, the top surface of the piston 2 is recessed downward for a distance to form a recessed area 21 open to the combustion chamber 31. Figure 1 As shown in the upper and lower directions, the recessed area 21 is open upward, and the central injector 4 and the side injector 5 are suitable for injecting fuel toward the recessed area 21 respectively, that is, in the intake stroke, the side injector 5 can inject fuel toward the recessed area 21, so that the oil beam of the side injector 5 can be sprayed into the recessed area 21; in the compression process, the central injector 4 can inject fuel toward the recessed area 21, so that the oil beam of the central injector 4 can be sprayed into the recessed area 21.

[0039] In practice, refer to the attached Figure 2 As shown, when the piston 2 moves to the vicinity of the top dead center, the air and the oil beam injected by the center injector 4 are mixed to form a mixture. At this time, ignition forms a flame, and the flame propagates to form a tumble. The mixture moves in a counterclockwise direction and reaches E of the recessed area 21 of the piston 2, moves along the recessed area 21, and flows out from F of the recessed area 21, thereby enhancing the tumble intensity and improving the turbulent kinetic energy, thereby forming stronger turbulence and tumble in the cylinder 1, thereby improving the combustion speed and combustion efficiency.

[0040] As a result, the fuel injected by the two injectors falls into the recessed area 21, so that the fuel can be more effectively distributed in the combustion chamber 31. Combined with the movement direction of the airflow, the mixture is made uniform, forming a gas that is more easily combustible, thereby improving the combustion speed and combustion efficiency, making the combustion speed faster and the combustion more complete, thereby improving the performance of the engine. At the same time, it can also enhance the tumble intensity and increase the turbulent kinetic energy.

[0041] According to the engine of the embodiment of the present invention, by arranging the central injector 4 and the side injector 5 to respectively inject fuel into the recessed area 21 of the piston 2, the uniformity of the mixture in the cylinder can be improved, the combustion speed can be accelerated, the fuel consumption can be reduced, and the emission of harmful substances can be reduced. At the same time, the tumble intensity can be enhanced and the turbulent kinetic energy can be improved.

[0042] In some embodiments, as Figure 1 As shown, the recessed area 21 is constructed as a circular area. The circular recessed area 21 is conducive to the fuel being evenly distributed in the recessed area 21 during injection, forming a more stable fuel-fuel mixture, thereby helping to improve the fuel economy and power performance of the engine. At the same time, the circular recessed area 21 is also easy to manufacture and process, reducing manufacturing costs.

[0043] like Figure 2 As shown, the diameter of the recessed area 21 is A1, the depth of the recessed area 21 is A2, and the following conditions are satisfied: 10≤A1 / A2≤16, that is, the ratio between the diameter A1 of the recessed area 21 and the depth A2 of the recessed area 21 can be set to 10, 11, 12, 13, 15, 16 or other ratios, which can be flexibly set according to actual conditions and is not limited to the present embodiment.

[0044] When the ratio between the diameter A1 of the recessed area 21 and the depth A2 of the recessed area 21 is too low, that is, the depth is too large, the fuel may not be fully atomized, resulting in incomplete combustion. When the ratio between the diameter A1 of the recessed area 21 and the depth A2 of the recessed area 21 is too high, that is, the diameter is too large or the depth is too small, sufficient vortex may not be formed to enhance combustion.

[0045] By setting the ratio between the diameter A1 of the recessed area 21 and the depth A2 of the recessed area 21 within a reasonable range of 10 to 16, it can be ensured that the oil beams injected by the center injector 4 and the side injector 5 can accurately fall within the diameter range of the recessed area 21, quickly mix with the air, and combine with the movement direction of the airflow to make the mixed gas more uniform, further improve the combustion speed and combustion efficiency, form a gas that is more easily burned, burn faster, and burn more completely, thereby reducing the emission of unburned fuel and harmful substances.

[0046] In a further embodiment, the following condition is satisfied: 12≤A1 / A2≤14, thereby further improving the uniformity of the mixture and increasing the full combustion effect, thereby further reducing the emission of unburned fuel and harmful substances and improving the fuel economy of the engine.

[0047] Specifically, A1 / A2 can be set to 12, 12.2, 12.3, 12.4, 12.5, 12.6, 13, 13.2, 13.4, 13.6, 13.8, 14, or other values ​​within this range. Within this range, the mixture achieves better uniformity. In other words, the fuel jets from the center injector 4 and the side injectors 5 can be more precisely injected within the diameter of the recessed area 21, thereby reducing the amount of fuel that falls outside the diameter of the recessed area 21. Furthermore, the fuel and air can be more fully mixed in accordance with the direction of airflow, thereby improving the uniformity of airflow mixing within the combustion chamber.

[0048] In some embodiments, as Figure 2 As shown, the injection range of the side injector 5 is B1, and the injection range of the center injector 4 is B2, and they satisfy: 1.2≤B1 / B2≤1.7, that is, the ratio between the injection range B1 of the side injector 5 and the injection range B2 of the center injector 4 can be set to 1.2, 1.3, 1.4, 1.5, 1.6, 1.7 or other ratios, which can be flexibly set according to actual conditions and is not limited to the description in this embodiment.

[0049] It can be understood that the larger B1 and B2 are, the larger the injection range of the side injector 5 and the injection range of the center injector 4 are, and the larger the coverage of the oil beams sprayed by the two injectors in the cylinder 1 is, but it may cause the fuel to fail to fall into the recessed area 21 and be unevenly distributed in the combustion chamber 31.

[0050] By setting the ratio between the injection range B1 of the side injector 5 and the injection range B2 of the center injector 4 within a reasonable range of 1.2 to 1.7, it is possible to ensure that the fuel is distributed more evenly in the combustion chamber 31, enhance the vortex and turbulence in the combustion chamber 31, thereby promoting the full combustion of the fuel. At the same time, specific combustion performance characteristics can be achieved, and the mixing and combustion process of the oil beam in the cylinder 1 can be controlled, thereby achieving the purpose of optimizing combustion efficiency, reducing emissions and improving engine performance.

[0051] Reference Attachment Figure 3 and attached Figure 4 As shown, the fuel and air mixture flow in cylinder 1 forms a rotating mixed flow. This flow includes radial and axial flow characteristics. Axial flow includes flow that diffuses outward from the plane axis as the center, while radial flow is flow that flows outward from the central axis of piston 2 as the center. The axial and radial flow characteristics can be further used to achieve stratified mixing of air and fuel. By changing the ratio of the injection ranges of the two injectors (i.e., the B1 / B2 ratio), the intensity of the axial and radial flows can be adjusted to achieve different combustion characteristics. For example, radial flow can be increased to promote uniform distribution of fuel in cylinder 1, while increasing axial flow can facilitate the accumulation of fuel around spark plug 6, forming a mixture that is easier to ignite.

[0052] In a further embodiment, the following condition is satisfied: 13.5≤B1 / B2≤15.5, thereby further improving the uniformity of fuel distribution in the combustion chamber 31 and more accurately achieving different combustion performance characteristics.

[0053] Specifically, B1 / B2 can be set to 13.5, 13.6, 13.7, 13.8, 13.9, 14, 14.1, 14.2, 14.3, 14.4, 14.5, 14.6, 14.7, 14.8, 14.9, 15.0, 15.1, 15.2, 15.3, 15.4, 15.5 or other values ​​within this range. The closer the B1 / B2 ratio is to a value between 13.5 and 15.5, the better the uniformity of fuel distribution in the combustion chamber 31, thereby better the uniformity of fuel mixing with air, and the easier it is to fully fuel the fuel. At the same time, the closer the B1 / B2 ratio is to a value within this range, the more accurately different combustion performance characteristics can be achieved, thereby further enabling stratified mixing of air and fuel to achieve desired combustion characteristics, ultimately achieving more complete combustion.

[0054] In some embodiments, an intake valve avoidance recess 22 and an exhaust valve avoidance recess 23 are further formed on the top surface of the piston 2 , and both the intake valve avoidance recess 22 and the exhaust valve avoidance recess 23 are spaced apart from the recess area 21 .

[0055] Specifically, if Figure 1 As shown, the top surface of the piston 2 is concave to form an intake valve avoidance recess 22 and an exhaust valve avoidance recess 23. The intake valve avoidance recess 22 is used to avoid the intake valve, so that when the piston 2 moves upward, the intake valve will not interfere with the piston 2. At the same time, it is ensured that the intake valve remains open when the piston 2 approaches its top to allow air to enter the cylinder 1 through the intake valve. Similarly, the exhaust valve avoidance recess 23 is used to avoid the exhaust valve, ensuring that when the piston 2 moves downward to discharge exhaust gas, the exhaust valve will not interfere with the top of the piston 2. At the same time, it is ensured that the exhaust valve remains open when the piston 2 approaches its bottom to smoothly discharge the exhaust gas after combustion.

[0056] like Figure 5 As shown, the intake valve avoidance recess 22 and the exhaust valve avoidance recess 23 are spaced apart from the recess area 21, and the intake valve avoidance recess 22 and the exhaust valve avoidance recess 23 are distributed around the recess area 21. This is conducive to uniform distribution of fuel in the combustion chamber 31, maximizing the effective space in the combustion chamber 31, thereby improving combustion efficiency and engine performance. At the same time, it avoids interference between the recess area 21 and the intake valve avoidance recess 22 and the exhaust valve avoidance recess 23, reducing the interference of the valve on the flow and mixing of fuel in the combustion chamber 31, thereby further improving the efficiency and stability of the engine.

[0057] In some embodiments, as Figure 5 As shown, the distance from the recessed area 21 to the intersection of the intake valve avoidance recess 22 and the top surface of the piston 2 is C1, and the distance from the recessed area 21 to the intersection of the exhaust valve avoidance recess 23 and the top surface of the piston 2 is C2, and satisfies: C1<C2, that is, the distance from the recessed area 21 to the intersection of the intake valve avoidance recess 22 and the top surface of the piston 2 is smaller than the distance from the recessed area 21 to the intersection of the exhaust valve avoidance recess 23 and the top surface of the piston 2. In other words, the distance from the recessed area 21 to the intersection of the intake valve avoidance recess 22 and the top surface of the piston 2 is closer, and the distance from the recessed area 21 to the intersection of the exhaust valve avoidance recess 23 and the top surface of the piston 2 is farther, thereby adapting to the layout of the intake valve and the exhaust valve on the cylinder head.

[0058] In some embodiments, the recessed area 21 is located in a central area of ​​the surface of the piston 2 facing the combustion chamber 31 .

[0059] Specifically, if Figure 1 and Figure 2 As shown, the recessed area 21 is located in the central area of ​​the top surface of the piston 2, that is, the central area of ​​the surface facing the combustion chamber 31. This arrangement ensures that the fuel can be evenly distributed in the combustion chamber 31 and fully mixed with the air, thereby improving combustion efficiency.

[0060] In some embodiments, a spark plug 6 is provided at the top of the combustion chamber 31 above the recessed area 21, the side injector 5 is suitable for injecting fuel into an area with a diameter outside a set diameter centered on the electrode of the spark plug 6, and the center injector 4 is suitable for injecting fuel into an area with a diameter within a set diameter centered on the electrode of the spark plug 6.

[0061] Specifically, if Figure 1 and Figure 2 As shown, a spark plug 6 is provided at the top of the combustion chamber 31 above the recessed area 21 , and the spark plug 6 is used to ignite the mixture in the cylinder 1 to achieve combustion of the mixture, thereby pushing the piston 2 to move and achieving normal operation of the engine.

[0062] During the intake stroke, the piston 2 moves downward, and the side injector 5 injects fuel into an area with a diameter outside the set diameter centered on the electrode of the spark plug 6 to perform in-cylinder atomization. By injecting fuel to the periphery of the electrode of the spark plug 6, it can be ensured that there is sufficient fuel distribution in the entire combustion chamber 31, thereby avoiding the situation of excessive or insufficient local fuel, which is conducive to uniform fuel distribution. Moreover, the spark plug 6 is located outside the injection range of the side injector 5, and the side injector 5 will not directly interfere with the ignition process of the spark plug 6 when injecting fuel, thereby improving the stability and reliability of the ignition.

[0063] When the piston 2 moves to the bottom dead center and then moves upward, when it reaches near the top dead center, the center injector 4 injects fuel into an area with a set diameter centered on the electrode of the spark plug 6, and determines the concentration of the mixture around the spark plug 6. The piston 2 continues to move upward for ignition. By directly injecting the fuel near the electrode of the spark plug 6, a combustible mixture can be formed more quickly, which is easier to be ignited by the spark plug 6, while reducing the generation of unburned fuel.

[0064] In some embodiments, the diameter is set to D and satisfies: 25 mm ≤ D ≤ 27 mm.

[0065] That is, the set diameter D can be set to 25 mm, 26 mm, 27 mm or other values, and can be flexibly set according to actual conditions, and is not limited to what is described in this embodiment.

[0066] The set diameter D affects the fuel concentration and the uniformity of the mixture near the spark plug 6. A properly set diameter can ensure that there is sufficient mixture around the spark plug 6, thereby improving the ignition efficiency. At the same time, the set diameter D will also affect the injection range and fuel distribution of the side injector 5, the injection accuracy of the center injector 4, and the uniformity of the mixture.

[0067] By setting the set diameter D within the range of 25mm to 27mm, it is possible to achieve that during the intake stroke, the side injector 5 injects fuel into an area with a diameter of 25mm to 27mm centered on the electrode of the spark plug 6, and performs in-cylinder atomization, so that the fuel can be evenly distributed around the electrode of the spark plug 6; and during the compression stroke, the center injector 4 injects fuel into an area with a diameter of 25mm to 27mm centered on the electrode of the spark plug 6, so that the fuel can be quickly mixed with the air to form a combustible mixture, ensuring that the concentration and uniformity of the mixture around the spark plug 6 are sufficient, thereby improving the ignition efficiency and achieving a faster and more uniform combustion process, thereby improving the output power and efficiency of the engine.

[0068] In the actual design, when the piston is moving downward, that is, when the engine is in the intake stroke, the crankshaft angle is 50 to 180°CA. At this time, the side injector 5 injects fuel into the area with a diameter of 25mm to 27mm centered on the electrode of the spark plug 6 to perform in-cylinder atomization. After reaching the bottom dead center, the piston moves upward. When it reaches the top dead center at 680 to 690°CA, the center injector 4 injects fuel into the area with a diameter of 25mm to 27mm centered on the electrode of the spark plug 6 to ensure sufficient mixture concentration around the spark plug. Then the piston continues to move upward at 690 to 700°CA for ignition.

[0069] In a further embodiment, the following condition is satisfied: 25.5mm≤D≤26.5mm. Thus, during the intake stroke, the side injector 5 can inject fuel outside the area with a diameter of 25.5mm to 26.5mm centered on the electrode of the spark plug 6, thereby performing sufficient in-cylinder atomization, so that the fuel is more evenly distributed around the electrode of the spark plug 6; and during the compression stroke, the center injector 4 can inject fuel into the area with a diameter of 25.5mm to 26.5mm centered on the electrode of the spark plug 6, so that the fuel can mix with the air more quickly to form a combustible mixture, thereby further improving the concentration and uniformity of the mixture around the spark plug 6.

[0070] Specifically, D can be set to 25.5, 25.52, 25.54, 25.56, 25.58, 25.6, 25.62, 25.64, 25.66, 25.7, 25.8, 25.9, 26, 26.1, 26.2, 26.3, 26.4, 26.5 or other values ​​within this range. It can be flexibly set according to actual conditions and is not limited to that described in this embodiment.

[0071] It can be understood that the closer the value is to the range of 25.5mm to 26.5mm, the better the uniformity of the fuel mixing in the combustion chamber, the higher the concentration of the mixture around the spark plug, and the more conducive it is to ignition and achieving full combustion.

[0072] In some embodiments, as Figure 2 As shown, the electrodes of the spark plug 6 include a first plate surface electrode 61 and a second plate surface electrode 62 that are relatively distributed in the up and down directions, the first plate surface electrode 61 is located at the top, and the second plate surface electrode 62 is located at the bottom. The first plate surface electrode 61 and the second plate surface electrode 62 are spaced a certain distance apart to form an electrode gap, and the first plate surface electrode 61 and the second plate surface electrode 62 are basically distributed parallel to each other to form a stable electrode gap. When the spark plug 6 is activated, a high-voltage electric spark is generated in the electrode gap, thereby igniting the combustible mixture in the cylinder 1.

[0073] The surface area of ​​the first plate electrode 61 is E1, and the surface area of ​​the second plate electrode 62 is E2, and they satisfy: 0.18≤E1 / E2≤0.3, that is, the ratio between the surface area E1 of the first plate electrode 61 and the surface area E2 of the second plate electrode 62 can be set to 0.18, 0.2, 0.25, 0.3 or other ratios, which can be flexibly set according to actual conditions and is not limited to the description in this embodiment.

[0074] By setting the ratio between the surface area E1 of the first plate electrode 61 and the surface area E2 of the second plate electrode 62 within a reasonable range of 0.18 to 0.3, it is ensured that the arc is evenly distributed in the electrode gap, thereby improving the ignition efficiency, allowing the mixture to burn more fully, improving the combustion efficiency, and reducing electrode wear and heat loss, thereby extending the service life of the spark plug 6.

[0075] In practice, when the fuel injected by the center injector 4 is mixed with air, a mixture with a concentration of 0.5 to 1.3 can be formed around the spark plug 6. The mixture in this concentration range is conducive to stable ignition and efficient combustion. At this time, ignition is performed to form a flame, and the flame propagates in the mixture to form a tumble flow. The mixture moves in a counterclockwise direction and reaches E of the recessed area 21 of the piston 2, moves along the recessed area 21, and flows out from F of the recessed area 21, thereby improving the effect of enhancing the tumble flow intensity and increasing the turbulent kinetic energy.

[0076] The utility model also provides a vehicle.

[0077] A vehicle according to an embodiment of the present invention includes an engine according to any one of the above embodiments.

[0078] By installing the above-mentioned engine in the vehicle, the mixture can be burned more fully due to the better mixing uniformity of the mixture, which is beneficial to improving the fuel economy of the engine and reducing the generation of harmful substances. The high tumble intensity and high turbulence can accelerate the propagation of flames, improve combustion efficiency, and increase the power output of the engine, thereby improving the vehicle's power performance, reducing fuel consumption, and reducing the vehicle's pollution to the environment.

[0079] Throughout this specification, reference to terms such as "one embodiment," "some embodiments," "illustrative embodiments," "examples," "specific examples," or "some examples" means that the specific features, structures, materials, or characteristics described in conjunction with that embodiment or example are included in at least one embodiment or example of the present invention. In this specification, the illustrative use of the above terms does 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 any one or more embodiments or examples.

[0080] Although the embodiments of the present invention have been shown and described, those skilled in the art will appreciate that various changes, modifications, substitutions and variations may be made to the embodiments without departing from the principles and purpose of the present invention, and that the scope of the present invention is defined by the claims and their equivalents.

Claims

1. An engine, characterized in that: include: a cylinder, wherein a movable piston is disposed in the cylinder, and a combustion chamber is defined between the piston and the cylinder; a central injector and a side injector, wherein the central injector and the side injector are both located at the top of the combustion chamber, and a distance between the central injector and the center of the top of the combustion chamber is smaller than a distance between the side injectors and the center of the top of the combustion chamber; A concave area open toward the combustion chamber is formed on the top surface of the piston, and the center injector and the side injector are suitable for injecting fuel toward the concave area respectively.

2. The engine according to claim 1, characterized in that The recessed area is configured as a circular area, a diameter of the recessed area is A1, a depth of the recessed area is A2, and the following relationship is satisfied: 10≤A1 / A2≤16.

3. The engine according to claim 2, characterized in that Satisfies: 12≤A1 / A2≤14.

4. The engine according to claim 1, characterized in that The injection range of the side injector is B1, the injection range of the center injector is B2, and the following conditions are satisfied: 1.2≤B1 / B2≤1.

7.

5. The engine according to claim 4, characterized in that Meet: 13.5≤B1 / B2≤15.

5.

6. The engine according to claim 1, characterized in that An intake valve avoidance recess and an exhaust valve avoidance recess are further formed on the top surface of the piston, and the intake valve avoidance recess and the exhaust valve avoidance recess are both spaced apart from the recess area.

7. The engine according to claim 6, characterized in that The distance from the recessed area to the intersection of the intake valve avoidance recess and the top surface of the piston is C1, and the distance from the recessed area to the intersection of the exhaust valve avoidance recess and the top surface of the piston is C2, and the relationship C1<C2 is satisfied.

8. The engine according to claim 1, characterized in that The recessed area is located in a central area of ​​a surface of the piston facing the interior of the combustion chamber.

9. The engine according to any one of claims 1 to 8, characterized in that A spark plug is provided at the top of the combustion chamber above the recessed area. The side injector is suitable for injecting fuel into an area with a diameter outside a set diameter centered on the electrode of the spark plug, and the center injector is suitable for injecting fuel into an area with a diameter within a set diameter centered on the electrode of the spark plug.

10. The engine according to claim 9, characterized in that The set diameter is D, and satisfies: 25mm≤D≤27mm.

11. The engine according to claim 10, characterized in that Meets: 25.5mm≤D≤26.5mm.

12. The engine according to claim 9, characterized in that The electrodes of the spark plug include a first plate surface electrode and a second plate surface electrode distributed relative to each other in the up and down directions, an electrode gap is formed between the first plate surface electrode and the second plate surface electrode, the surface area of ​​the first plate surface electrode is E1, the surface area of ​​the second plate surface electrode is E2, and the following is satisfied: 0.18≤E1 / E2≤0.

3.

13. A vehicle, characterized in that: The engine comprises the engine according to any one of claims 1-12.

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