Cylinder cover assembly and vehicle

Abstract

The utility model discloses a cylinder cover assembly and a vehicle, the cylinder cover assembly comprises a cylinder cover, the cylinder cover is provided with an air inlet and an air outlet, and the air inlet is used for installing an air inlet valve guide pipe; the air inlet pipe is connected to the cylinder cover, an air inlet throat and an air inlet flow channel are formed in the air inlet pipe, and the air inlet flow channel communicates with the air inlet through the air inlet throat; an included angle is formed between the center line of the air inlet valve guide pipe and the center line of the air inlet flow channel, and a flow guide face is formed on the inner bottom wall of the air inlet flow channel and used for guiding air flow to flow from the inner top wall of the air inlet throat opening to the air inlet. According to the cylinder cover assembly, strong tumble flow can be formed in the combustion chamber, turbulent kinetic energy in the cylinder is improved, and therefore air and fuel can be fully and evenly mixed, the combustion speed and the heat efficiency are improved, and generation of incompletely-combusted products is reduced.

Description

Technical Field

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

[0002] To ensure the automotive industry develops in a more sustainable direction, emission regulations are constantly being upgraded around the world. Improving engine thermal efficiency is a key measure, and therefore, all companies conduct detailed, comprehensive, and multi-round design verification of their engine combustion systems to achieve high thermal efficiency targets. The engine's intake structure affects intake resistance, charging efficiency, and in-cylinder gas flow. Its design directly impacts the engine's power, economy, and emissions. The intake structure primarily consists of the intake duct and cylinder head combustion chamber. Conventional evaluation methods for intake structures include steady-state CFD calculations (calculating the tumble ratio and flow coefficient) and transient CFD calculations (evaluating in-cylinder flow). A higher tumble ratio creates greater turbulent kinetic energy within the cylinder, facilitating fuel-gas mixing, improving thermal efficiency, and enhancing power. Furthermore, a stronger in-cylinder flow field reduces the likelihood of pre-ignition and detonation.

[0003] The existing cylinder head assembly has a poor effect on the turbulent kinetic energy generated in the cylinder, and there is room for improvement. Utility Model Content

[0004] 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 a cylinder head assembly that can generate a strong tumble flow within the combustion chamber, increasing the turbulent kinetic energy within the cylinder, thereby facilitating a thorough and uniform mixing of air and fuel, improving combustion speed and thermal efficiency, and reducing the generation of incomplete combustion products.

[0005] According to an embodiment of the present invention, a cylinder head assembly includes: a cylinder head, the cylinder head is provided with an air intake port and an exhaust port, the air intake port is used to install an intake valve guide; an intake pipe, the intake pipe is connected to the cylinder head, an intake throat and an intake flow channel are formed in the intake pipe, the intake flow channel is connected to the air intake port through the intake throat; wherein the center line of the intake valve guide forms an angle with the center line of the intake flow channel, and the inner bottom wall of the intake flow channel is formed with a guide surface, the guide surface is used to guide the airflow to flow from the inner top wall of the intake throat toward the air intake.

[0006] According to the cylinder head assembly of the embodiment of the present invention, by making the center line of the intake valve guide form an angle with the center line of the intake flow channel, the flow direction of the gas can be changed, turbulence and flow resistance can be reduced, and the intake efficiency can be improved, so that the air can enter the combustion chamber more smoothly, evenly and quickly; a guide surface is set on the inner bottom wall of the intake flow channel to guide the airflow from the inner top wall of the intake throat toward the intake port, so that a strong tumble flow can be formed in the combustion chamber, and the turbulent kinetic energy in the cylinder is increased, which is beneficial to the full and uniform mixing of air and fuel, improves the combustion speed and thermal efficiency, and reduces the generation of incomplete combustion products.

[0007] According to the cylinder head assembly of some embodiments of the present invention, the angle between the center line of the intake valve guide and the center line of the intake flow passage is A1, and satisfies: 40°≤A1≤45°.

[0008] According to some embodiments of the present invention, the cylinder head assembly satisfies the following: 42.5°≤A1≤43.5°.

[0009] According to the cylinder head assembly of some embodiments of the present invention, the intake flow duct is connected to the side of the intake throat away from the exhaust port; the angle between the tangent of the guide surface at the end connected to the intake throat and the parallel line of the bottom surface of the exhaust port is A2, and satisfies: 150°≤A2≤165°.

[0010] According to some embodiments of the present invention, the cylinder head assembly satisfies the following conditions: 155°≤A2≤160°

[0011] According to the cylinder head assembly of some embodiments of the present invention, there are two air inlets and two exhaust ports distributed in one-to-one correspondence; there are two air intake pipes connected to the two air inlets in one-to-one correspondence, and the two air intake pipes extend obliquely in a direction close to the air inlet toward a direction away from each other.

[0012] According to the cylinder head assembly of some embodiments of the present invention, the angle between the extension directions of the two intake pipes is A3, and satisfies: 14°≤A3≤20°.

[0013] According to some embodiments of the present invention, the cylinder head assembly satisfies the following conditions: 14°≤A3≤18°.

[0014] According to the cylinder head assembly of some embodiments of the present invention, the air inlet and the corresponding exhaust port are spaced apart along a first direction, and the two air inlets are spaced apart along a second direction, and the second direction intersects with the first direction; wherein, the cylinder head is formed with air-guiding side walls at both side edges in the second direction, and the two air-guiding side walls extend obliquely toward each other along the direction from the air inlet to the exhaust port.

[0015] According to the cylinder head assembly of some embodiments of the present invention, the angle between the extension directions of the two gas guide side walls is A4, and satisfies: 10°≤A4≤20°.

[0016] According to some embodiments of the present invention, the cylinder head assembly satisfies the following conditions: 13°≤A4≤17°.

[0017] According to the cylinder head assembly of some embodiments of the present invention, the angle between the air guide side wall and the extension direction of the intake pipe on the same side is A5, and satisfies: 10°≤A5≤20°.

[0018] According to some embodiments of the present invention, the cylinder head assembly satisfies the following conditions: 13°≤A5≤17°.

[0019] According to the cylinder head assembly of some embodiments of the present invention, the center line of the intake throat coincides with the center line of the intake valve guide.

[0020] The utility model also provides a vehicle.

[0021] A vehicle according to an embodiment of the present invention includes the cylinder head assembly described in any one of the above embodiments.

[0022] The advantages of the vehicle and the cylinder head assembly described above over the prior art are the same and will not be described in detail here.

[0023] 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

[0024] 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:

[0025] Figure 1 It is a schematic diagram of the gas flow in the cylinder head assembly of the prior art;

[0026] Figure 2 This is a schematic diagram of the structure of the cylinder head assembly according to an embodiment of the present utility model. Figure 1 ;

[0027] Figure 3 This is a schematic diagram of the structure of the cylinder head assembly according to an embodiment of the present utility model. Figure 2 ;

[0028] Figure 4 This is a cross-section of a cylinder head assembly according to an embodiment of the present invention. Figure 1 ;

[0029] Figure 5 This is a cross-section of a cylinder head assembly according to an embodiment of the present invention. Figure 2 ;

[0030] Figure 6 Schematic diagram of gas flow in a cylinder head assembly according to an embodiment of the present utility model;

[0031] Figure 7 This is a cross-section of a cylinder head assembly according to an embodiment of the present invention. Figure 3 ;

[0032] Figure 8 This is a CFD simulation result 1 of a cylinder head assembly according to an embodiment of the present utility model;

[0033] Figure 9 This is the second CFD simulation result of the cylinder head assembly according to the embodiment of the present utility model.

[0034] Reference numerals:

[0035] Cylinder head assembly 100,

[0036] Cylinder head 1, air intake 11, exhaust port 12, air guide side wall 13,

[0037] Intake pipe 2, intake throat 21, intake flow channel 22, guide surface 221, piston 3, piston combustion chamber 31, intake valve guide 4. DETAILED DESCRIPTION

[0038] 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.

[0039] 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.

[0040] 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.

[0041] 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.

[0042] First of all, it should be noted that the traditional cylinder head assembly is also provided with an intake pipe, in which an intake flow channel is formed. Air can flow to the intake port through the intake flow channel and then directly enter the combustion chamber. However, this gas flow direction cannot form a strong tumble flow in the combustion chamber, resulting in poor turbulent kinetic energy in the cylinder, and the air cannot be fully and evenly mixed with the fuel, resulting in poor engine fuel economy.

[0043] The present utility model proposes a cylinder head assembly 100, which can guide the air through the guide surface 221 during the intake process of the air through the air intake port 11, so that the air flow flows from the inner top wall of the intake throat 21 toward the air intake port 11, so as to form a strong tumble flow in the combustion chamber, increase the turbulent kinetic energy in the cylinder, thereby facilitating the full and uniform mixing of air and fuel, improving the combustion speed and thermal efficiency, and reducing the generation of incomplete combustion products.

[0044] like Figures 1-9 As shown, a cylinder head assembly 100 according to an embodiment of the present invention includes: a cylinder head 1 and an intake pipe 2.

[0045] The cylinder head 1 is installed above the cylinder block, sealing the cylinder from the top and forming a combustion chamber together with the cylinder block. The cylinder head 1 is provided with an intake port 11 and an exhaust port 12. The intake port 11 is used to install an intake valve guide 4. The intake valve guide 4 can guide the movement of the intake valve to ensure that the intake valve performs reciprocating linear motion and correctly fits the intake valve and the intake valve seat ring, thereby ensuring the precise movement and sealing performance of the intake valve. Among them, the intake port 11 can inhale air and allow it to enter the combustion chamber, that is, air can enter the combustion chamber through the intake port 11, and the exhaust port 12 is used to discharge exhaust gas generated after combustion and allow it to leave the combustion chamber, that is, exhaust gas can leave the combustion chamber through the exhaust port 12.

[0046] The intake pipe 2 is connected to the cylinder head 1 . An intake throat 21 and an intake flow passage 22 are formed in the intake pipe 2 . The intake flow passage 22 is connected to the intake port 11 through the intake throat 21 .

[0047] Specifically, refer to the attached Figure 2 and attached Figure 4 As shown, the intake pipe 2 is connected to the top of the cylinder head 1 and is used to guide air into the cylinder. The intake pipe 2 extends upward, and an intake throat 21 and an intake flow channel 22 are formed inside it. The intake flow channel 22 is the main flow path of air. The intake throat 21 is an expanded part inside the intake pipe 2, which can improve the air flow efficiency and the engine's intake capacity, allowing a large amount of gas to enter the combustion chamber.

[0048] Among them, the air intake throat 21 and the intake flow channel 22 are connected to form an air flow channel together. The air intake throat 21 is located below the intake flow channel 22. The intake flow channel 22 is connected with the air intake port 11 through the air intake throat 21, that is, the air can flow from the intake flow channel 22 to the air intake throat 21, and then flow from the air intake throat 21 to the air intake port 11, and enter the combustion chamber through the air intake port 11 for combustion.

[0049] Furthermore, the centerline of the intake valve guide 4 forms an angle with the centerline of the intake air duct 22 , and the inner bottom wall of the intake air duct 22 is formed with a guide surface 221 , which is used to guide the airflow from the inner top wall of the intake throat 21 toward the intake port 11 .

[0050] Specifically, refer to the attached Figure 4 As shown, the center line of the intake valve guide 4 forms an angle with the center line of the intake flow passage 22, that is, the center line of the intake valve guide 4 and the center line of the intake flow passage 22 are not on the same straight line, but there is a certain deflection angle. Figure 4 The angle shown in the figure is an acute angle, which is conducive to changing the flow direction of the gas and generating a rotation or vortex effect before the gas enters the air intake 11, while reducing turbulence and flow resistance, improving the intake efficiency, so that the air can enter the combustion chamber more smoothly, evenly and quickly to be fully and evenly mixed with the fuel, thereby reducing the generation of incomplete combustion products, reducing the emission level of the engine, and helping to meet increasingly stringent environmental protection standards.

[0051] Reference Attachment Figure 5 As shown, the inner bottom wall of the inlet air flow channel 22 is formed with a guide surface 221, which can guide the air flow to flow upward ( Figure 5 The direction of the arrow shown in the figure is the direction of air flow) and flows to the inner top wall of the intake throat 21, flows along the inner top wall of the intake throat 21 to the intake port 11, and then smoothly enters the combustion chamber, which can ensure that the positive airflow adheres to the inner wall surface of the combustion chamber of the cylinder head 1 and transitions to the exhaust port 12, and then downwardly enters the cylinder, forming a strong tumble flow, increasing the turbulent kinetic energy in the cylinder, further promoting the full mixing and combustion of fuel and air, improving the combustion speed and thermal efficiency, and reducing the generation of incomplete combustion products.

[0052] According to the cylinder head assembly 100 of the embodiment of the present invention, by forming an angle between the center line of the intake valve guide 4 and the center line of the intake flow channel 22, the flow direction of the gas can be changed, turbulence and flow resistance can be reduced, and the intake efficiency can be improved, so that the air can enter the combustion chamber more smoothly, evenly and quickly; a guide surface 221 is set on the inner bottom wall of the intake flow channel 22 to guide the air flow from the inner top wall of the intake throat 21 toward the intake port 11, so that a strong tumble flow can be formed in the combustion chamber, and the turbulent kinetic energy in the cylinder is increased, which is beneficial to the full and uniform mixing of air and fuel, improves the combustion speed and thermal efficiency, and reduces the generation of incomplete combustion products.

[0053] In some embodiments, as Figure 5 As shown, the angle between the center line of the intake valve guide 4 and the center line of the intake runner 22 is A1, and satisfies: 40°≤A1≤45°, that is, A1 can be set to 40°, 41°, 42°, 43°, 44°, 45° or other angles. It can be understood that, the larger the setting of A1, the larger the angle between the center line of the intake throat 21 and the center line of the intake runner 22, that is, the larger the relative offset angle between the intake throat 21 and the intake runner 22; the smaller the setting of A2, the smaller the angle between the center line of the intake throat 21 and the center line of the intake runner 22, that is, the smaller the relative offset angle between the intake throat 21 and the intake runner 22.

[0054] By setting the angle A1 between the center line of the intake throat 21 and the center line of the intake flow channel 22 within the range of 40° to 45°, it can be ensured that the airflow can generate sufficient rotation or vortex effect before entering the combustion chamber. At the same time, excessive deflection of the airflow is limited to avoid excessive turbulence and flow resistance, so that the gas can enter the combustion chamber more smoothly and efficiently, further improving the intake efficiency, and mixing with the fuel more fully and evenly in the combustion chamber, improving the mixing effect of oil and gas, and allowing the fuel to be fully and quickly burned, thereby reducing the generation of unburned products.

[0055] In a further embodiment, the following is satisfied: 42.5°≤A1≤43.5°, so that the airflow can generate a better rotation or vortex effect before entering the combustion chamber. Specifically, A1 can be set to 42.5°, 42.52°, 42.53°, 42.54°, 42.6°, 42.63°, 42.65°, 42.68°, 42.88°, 43°, 43.2°, 43.3°, 43.4°, 43.5°, or other degrees.

[0056] It should be noted that the closer the value of A1 is to the value within the range of 42.5° to 43.5°, the better the rotation or vortex effect that the airflow can produce before entering the combustion chamber, which can improve the mixing effect of oil and gas and enhance the uniformity of the airflow mixing in the combustion chamber.

[0057] In some embodiments, the intake air duct 22 is connected to the side of the intake throat 21 away from the exhaust port 12; the angle between the tangent of the guide surface 221 at the end connected to the intake throat 21 and the parallel line of the bottom surface of the exhaust port 12 is A2, and satisfies: 150°≤A2≤165°.

[0058] Specifically, if Figure 5 As shown, the intake flow duct 22 is connected to the upper right side of the intake throat 21, that is, the side away from the exhaust port 12. In this way, the interference of the exhaust flow on the intake flow can be minimized, and interference between the intake flow duct 22 and the exhaust flow duct can be avoided, thereby ensuring the stability of the intake process.

[0059] like Figure 5 As shown, the angle between the tangent line of the guide surface 221 at the end connected to the air inlet throat 21 and the parallel line of the bottom surface of the exhaust port 12 is A2. Figure 5 The endpoint where the guide surface 221 is connected to the air intake throat 21 is point D, and the tangent line is the left extension line of point D. An angle A2 is formed between the guide surface 221 and the parallel line to the bottom surface of the exhaust port 12. A2 determines how the guide surface 221 guides the airflow into the combustion chamber. The angle A2 satisfies: 150°≤A2≤165°, that is, the angle A2 can be set to 150°, 153°, 154°, 155°, 156°, 157°, 158°, 159°, 160°, 161°, 162°, 163°, 164°, 165° and other angles. It can be understood that the larger the A2 setting is, the larger the relative offset angle between the tangent of the guide surface 221 at the end connected to the air intake throat 21 and the parallel line of the bottom surface of the exhaust port 12 is, and the smaller the A2 setting is, the smaller the relative offset angle between the tangent of the guide surface 221 at the end connected to the air intake throat 21 and the parallel line of the bottom surface of the exhaust port 12 is.

[0060] By setting A2 within the range of 150° to 165°, the airflow can flow more smoothly to the combustion chamber, reducing the impact and friction of the airflow on the guide surface 221. At the same time, it can ensure to the greatest extent that the positive airflow adheres to the inner wall of the combustion chamber of the cylinder head 1 and enters the cylinder, thereby enhancing the effect of forming a strong tumble flow and thus increasing the turbulent kinetic energy in the cylinder.

[0061] In a further embodiment, the following is satisfied: 155°≤A2≤160°, thereby further enhancing the effect of forming a strong tumble flow and further increasing the turbulent kinetic energy in the cylinder. Specifically, A2 can be set to 155°, 155.2°, 155.24°, 155.3°, 155.36°, 155.41°, 155.42°, 155.48°, 155.5°, 155.52°, 155.4°, 155.47°, 155.5°, 155.54°, 155.6°, 155.69°, 155.7°, 155.77°, 155.8°, 155.91°, 155.93°, 155.94°, 155.95°, 155.96°, 155.97°, 155.98°, 155.99°, 155.99°, 155.91 ...3°, 155.94°, 155.95°, 155.96°, 155.97°, 155.98°, 155 .87°, 155.9°, 155.95°, 160° or other values ​​within this range, so that the airflow can be better guided, so that the airflow flows to the combustion chamber more smoothly and stably, reducing the impact and friction of the airflow on the guide surface 221, reducing the energy loss of the airflow, and at the same time, further ensuring to the greatest extent that the positive airflow fits the inner wall of the combustion chamber of the cylinder head 1 into the cylinder, enhancing the effect of forming a stronger tumble flow, thereby further improving the turbulent kinetic energy in the cylinder.

[0062] In some embodiments, there are two air inlets 11 and two air outlets 12 , and they are distributed in a one-to-one correspondence.

[0063] like Figure 2 As shown, the cylinder head 1 is provided with two air intake ports 11 and two exhaust ports 12. The provision of two air intake ports 11 can increase the air intake area and increase the amount of air entering the combustion chamber, so that the fuel and air can be more fully mixed, the combustion efficiency can be improved, and the generation of harmful gases such as CO can be reduced; similarly, the provision of two exhaust ports 12 can increase the exhaust area and accelerate the exhaust gas emission speed, thereby reducing the amount of residual exhaust gas in the combustion chamber, providing more space for the next air intake, and thus improving the ventilation effect of the engine.

[0064] The distribution of one intake port 11 corresponding to one exhaust port 12 can make the intake and exhaust processes of the cylinder more balanced, thereby reducing the pressure fluctuation in the cylinder and improving the stability and reliability of the engine. The two intake ports 11 and the two exhaust ports 12 can be opened and closed at the same time, thereby ensuring that the gas in the cylinder is quickly and completely replaced, improving the ventilation efficiency, and helping to reduce the amount of residual exhaust gas in combustion and reduce the emission of harmful gases such as CO.

[0065] Furthermore, there are two air inlet pipes 2 connected to the two air inlets 11 in a one-to-one correspondence, and the two air inlet pipes 2 extend obliquely from a direction close to the air inlet 11 toward a direction away from each other.

[0066] Specifically, if Figure 2As shown, the shape and size of the air intake pipe 2 are adapted to the air intake port 11, and each air intake port 11 is connected to an air intake pipe 2, and the two air intake pipes 2 extend obliquely in the direction close to the air intake port 11 toward the direction away from each other, that is, the closer the two air intake pipes 2 are to the two air intake ports 11, the greater the distance between them, and correspondingly, the farther the two air intake pipes 2 are from the two air intake ports 11, the smaller the distance between them.

[0067] It should be noted that, Figure 1 As shown, in the existing cylinder head 1, since the airflow velocity in the center of the combustion chamber is relatively high and the airflow velocity on both sides is relatively low, the airflow is unevenly distributed, resulting in that a relatively straight tumble rotation center line cannot be formed inside the combustion chamber.

[0068] By arranging the two air inlet pipes 2 to extend obliquely from the direction close to the air inlet 11 to the direction away from each other, as shown in FIG. Figure 6 As shown, a certain angle can be formed between the two intake pipes 2, which can guide the gas flow to both sides of the combustion chamber to increase the flow rate of the gas on both sides of the combustion chamber, which is conducive to making the flow rate of the gas on both sides of the combustion chamber equivalent to the flow rate of the gas in the middle, thereby facilitating the formation of a relatively straight tumble rotation center line in the center of the cylinder. Figure 6 The tumble flow rotation centerline shown in the figure is a horizontal line perpendicular to the direction of gas flow from the intake port 11 to the exhaust port 12. This tumble flow rotation centerline ensures that the tumble flow is maintained until the moment before ignition, preserving its angular momentum as much as possible, achieving repeatable charge motion, and reducing cycle-to-cycle variability. This promotes flame propagation uniformity, improves fuel mixing efficiency and combustion stability, facilitates exhaust gas discharge within the cylinder, and increases turbulent kinetic energy within the cylinder, thereby improving thermal efficiency, reducing the probability of knock, and reducing emissions of harmful gases such as CO.

[0069] In some embodiments, as Figure 3 As shown, the angle A3 between the extension directions of the two intake pipes 2 is satisfied: 14°≤A3≤20°, that is, the angle A3 between the extension directions of the intake pipes 2 can be set to 14°, 15°, 16°, 17°, 18°, 19°, 20° or other angles, and can be flexibly set according to actual needs, and is not limited to the description in this embodiment.

[0070] It can be understood that the larger the A3 is set, the larger the angle between the two intake pipes 2 is, and the easier it is for the airflow to flow to the sides of the combustion chamber. The smaller the A3 is set, the smaller the angle between the two intake pipes 2 is, and the weaker the effect of the airflow flowing to the sides of the combustion chamber is. However, A3 should not be too large or too small to avoid affecting the formation of the tumble effect.

[0071] By setting the angle A3 between the extension directions of the two intake pipes 2 within a reasonable range of 14° to 20°, it can be effectively ensured that the airflow flows to both sides of the combustion chamber in the most appropriate way, so that the flow rate of the gas on both sides of the combustion chamber is equivalent to the flow rate of the gas in the middle, avoiding the gas flow rate on both sides of the combustion chamber being too small to be equivalent to the flow rate of the gas in the middle, thereby facilitating the formation of a relatively straight tumble rotation centerline in the center of the cylinder.

[0072] In a further embodiment, the following is satisfied: 14°≤A3≤18°, thereby further improving the effect of making the flow rate of the gas on both sides of the combustion chamber equivalent to the flow rate of the gas in the middle, thereby enhancing the effect of forming a relatively straight tumble rotation centerline in the center of the cylinder.

[0073] Specifically, A3 can be set to 14°, 14.4°, 14.5°, 14.6°, 14.8°, 15°, 15.24°, 15.36°, 15.44°, 15.6°, 15.7°, 15.87°, 15.9°, 16°, 16.3°, 16.4°, 16.6°, 16.7°, 16.8°, 16.9°, 17°, 17.2°, 17.3°, 17.4°, 17.58°, 17.6°, 17.88°, 17.9°, 18° or other values ​​within the range. In this way, the airflow can be better guided so that the airflow flows to both sides of the combustion chamber through inertia, and is more accurately equivalent to the gas flow rate in the middle, thereby enhancing the effect of forming a relatively straight tumble rotation centerline in the center of the cylinder.

[0074] In some embodiments, the air inlet 11 and the corresponding air outlet 12 are spaced apart along a first direction, and the two air inlets 11 are spaced apart along a second direction, the second direction intersects the first direction, and the first direction may or may not intersect the second direction perpendicularly.

[0075] like Figure 2 As shown, Figure 2 In the example, the second direction intersects the first direction perpendicularly. The first direction corresponds to Figure 2 The up and down directions in the second direction correspond to Figure 2 In the left and right directions, the two air inlets 11 and the two exhaust ports 12 are spaced a certain distance apart in the left and right directions, the air inlet 11 on the left and the corresponding exhaust ports 12 on the left are spaced a certain distance apart in the up and down directions, and the air inlet 11 on the right and the corresponding exhaust ports 12 on the right are spaced a certain distance apart in the up and down directions.

[0076] Furthermore, air guiding side walls 13 are formed at both side edges of the cylinder head 1 in the second direction, and the two air guiding side walls 13 extend obliquely toward each other along the direction from the air inlet 11 to the exhaust port 12 .

[0077] Specifically, if Figure 2 As shown, the cylinder head 1 is Figure 2 Air guide side walls 13 are formed at both sides of the left and right sides of the middle portion. The two air guide side walls 13 extend from the air inlet 11 to the exhaust port 12 (ie, Figure 2 That is, the distance between the two air-guiding side walls 13 gradually decreases along the direction from the air inlet 11 to the exhaust port 12, and the air-guiding side walls 13 have a certain inclination.

[0078] Therefore, in practice, the gas flowing out of the two intake pipes 2 and toward the two sides of the combustion chamber will accelerate its flow speed when encountering the inclined inward-retracting gas guide side wall 13, thereby increasing the gas flow rate on both sides of the combustion chamber, and the superposition speed of the two gases flowing out of the two intake pipes 2 in the middle will slow down accordingly, so that the gas flow rate on both sides of the combustion chamber and the middle can be made equivalent, so that a relatively straight tumble rotation center line is formed in the center of the cylinder, so that the tumble can be maintained until the moment before ignition, retaining its angular momentum as much as possible, and realizing repeatable charging motion, while reducing changes between cycles, which is beneficial to the uniformity of flame propagation, improving fuel mixing efficiency and combustion stability, promoting the discharge of exhaust gas in the cylinder, and increasing the turbulent kinetic energy in the cylinder, thereby improving thermal efficiency, reducing the probability of knock, and reducing the emission of harmful gases such as CO.

[0079] In some embodiments, as shown in the figure, the angle A4 between the extension directions of the two air-guiding side walls 13 is satisfied: 10°≤A4≤20°, that is, the angle A4 between the extension directions of the two air-guiding side walls 13 can be set to 10°, 11°, 12°, 13°, 14°, 15°, 16°, 17°, 18°, 19°, 20° or other angles, which can be flexibly set according to actual conditions and is not limited to the present embodiment.

[0080] It can be understood that the larger the A4 is set, the greater the inclination of the two air-guiding side walls 13, that is, the larger the distance between the two air-guiding side walls 13 at the air inlet 11, and the smaller the distance between the two air-guiding side walls 13 at the exhaust port 12, which can guide the gas to flow faster, but it should not be too large to avoid affecting the tumbling effect of the gas.

[0081] By setting the angle A4 between the extension directions of the two gas-guiding side walls 13 within the range of 10° to 20°, the best gas flow effect can be achieved, that is, the gas flow rate flowing out of the intake pipe 2 to the two sides of the combustion chamber is equivalent to the gas flow rate in the middle, and the difference between the gas flow rate on both sides and the gas flow rate in the middle is very small, so as to form a relatively straight tumble rotation centerline in the center of the cylinder.

[0082] In a further embodiment, the following condition is satisfied: 13°≤A4≤17°, thereby further improving the guiding effect of the two air-guiding side walls 13 on the airflow, enhancing the effect that the gas flow velocity on both sides is equivalent to the gas flow velocity in the middle, that is, further reducing the difference between the gas flow velocity on both sides and the gas flow velocity in the middle, so as to form a straighter tumble rotation centerline, and further improving the tumble effect.

[0083] Specifically, A4 can be set to 13°, 13.2°, 13.4°, 13.6°, 13.8°, 14°, 14.2°, 14.4°, 14.6°, 14.7°, 14.8°, 14.9°, 15°, 15.2°, 15.4°, 15.6°, 15.7°, 15.9°, 16°, 16.2°, 16.4°, 16.6°, 16.8°, 17° or other values ​​within the range. In this way, the gas flowing out of the intake pipe 2 can flow along the gas guide side wall 13 inclined at a certain angle, thereby flowing to both sides faster, so as to more accurately increase the flow velocity of the gas on both sides, make the difference between the flow velocity of the gas on both sides and the flow velocity of the gas in the middle smaller, so as to form a straighter tumble rotation center line, and further enhance the tumble effect.

[0084] In some embodiments, as Figure 3 As shown, the angle A5 between the air-guiding side wall 13 and the extension direction of the air intake pipe 2 on the same side is satisfied: 10°≤A5≤20°, that is, the angle A5 between the air-guiding side wall 13 and the extension direction of the air intake pipe 2 on the same side can be set to 10°, 11°, 12°, 13°, 14°, 15°, 16°, 17°, 18°, 19°20° or other angles, which can be flexibly set according to actual conditions and is not limited to the present embodiment.

[0085] By setting the angle A5 between the air guide side wall 13 and the extension direction of the intake pipe 2 on the same side within the range of 10° to 20°, the gas can smoothly enter both sides of the combustion chamber while accelerating its flow speed and ensuring its smooth flow, avoiding excessive flow resistance caused by A5 being too large.

[0086] In a further embodiment, the following is satisfied: 13°≤A5≤17°, thereby further improving the gas flow effect, that is, further accelerating the flow speed of the gas, while further ensuring its flow stability, reducing flow resistance, making it easier to form large-scale tumble flow, thereby helping to improve the tumble effect. Specifically, A5 can be set to 13°, 13.2°, 13.4°, 13.6°, 13.8°, 13.9°, 14°, 14.2°, 14.4°, 14.6°, 14.8°, 15°, 15.2°, 15.4°, 15.6°, 16°, 16.2°, 16.4°, 16.6°, 16.8°, 17° or other values ​​within this range, and can be flexibly set according to actual conditions and is not limited to those described in this embodiment.

[0087] In some embodiments, as Figure 4 As shown, the center line of the intake throat 21 coincides with the center line of the intake valve guide 4 .

[0088] In this way, the gas can maintain a consistent flow direction when flowing through the air inlet throat 21 into the air inlet 11, thereby reducing the flow resistance of the gas from the air inlet throat 21 to the air inlet 11, allowing the gas to flow quickly from the air inlet throat 21 to the air inlet 11, increasing the air intake volume and improving the flow efficiency.

[0089] In some embodiments, as Figure 7 As shown, the piston combustion chamber 31 is matched with the combustion chamber of the cylinder head 1 so that the piston combustion chamber 31 and the combustion chamber of the cylinder head 1 can form a "clam-shaped" combustion chamber as a whole. Figure 7 The piston combustion chamber 31 shown in FIG is a spherical top surface piston 3.

[0090] In this way, during the intake process, the gas can flow along the inner wall of the combustion chamber of the cylinder head 1 at the intake port 11, transition to the exhaust port 12, and then flow downward into the pit of the piston combustion chamber 31, forming a strong positive tumble flow, ensuring that the large-scale strong tumble flow remains intact before ignition and is not broken up, thereby increasing the turbulent kinetic energy in the cylinder, and helping to improve the uniformity of flame propagation at the ignition moment, thereby increasing the combustion speed and combustion uniformity, reducing the probability of knock, ensuring that the mixture is fully burned, and improving thermal efficiency.

[0091] In actual design, the top surface of the piston 3 is as smooth as possible to reduce the loss of the flow field during the flow process.

[0092] like Figure 8 and Figure 9As shown, it is the CFD simulation result of different combustion chamber arrangements of the cylinder head assembly 100 of the present invention under the same working conditions (same compression ratio, same intake and exhaust ports and wrap angle). The curve before optimization is the CFD simulation result of the prior art, and the curve after optimization is the CFD simulation result of the present invention. It can be seen that the turbulent kinetic energy in the cylinder can be significantly improved after the ignition timing is optimized.

[0093] The utility model also provides a vehicle.

[0094] A vehicle according to an embodiment of the present invention includes the cylinder head assembly 100 according to any one of the above embodiments.

[0095] In the cylinder head assembly 100, by making the center line of the intake throat 21 form an angle with the center line of the intake flow channel 22, the flow direction of the gas can be changed, turbulence and flow resistance can be reduced, and the intake efficiency can be improved, so that the air can enter the combustion chamber more smoothly, evenly and quickly; a guide surface 221 is set on the inner bottom wall of the intake flow channel 22 to guide the airflow from the inner top wall of the intake throat 21 toward the intake port 11, which can form a strong tumble flow in the combustion chamber, increase the turbulent kinetic energy in the cylinder, thereby facilitating the full and uniform mixing of air and fuel, improving the combustion speed and thermal efficiency, and reducing the generation of incomplete combustion products.

[0096] By installing the above-mentioned cylinder head assembly 100 that can achieve high turbulent kinetic energy, low knock probability and high thermal efficiency in the vehicle, the engine can generate greater power, the vehicle can accelerate faster, travel more smoothly, and the reliability and durability of the vehicle can be improved. At the same time, the fuel economy of the vehicle can be improved and the fuel cost can be reduced.

[0097] 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.

[0098] 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. A cylinder head assembly, characterized in that: include: a cylinder head, wherein the cylinder head is provided with an air intake port and an exhaust port, wherein the air intake port is used for installing an intake valve guide; an intake pipe connected to the cylinder head, wherein an intake throat and an intake flow passage are formed in the intake pipe, and the intake flow passage is connected to the intake port through the intake throat; The center line of the intake valve guide forms an angle with the center line of the intake air duct, and the inner bottom wall of the intake air duct is formed with a guide surface, which is used to guide the airflow from the inner top wall of the intake throat toward the intake port.

2. The cylinder head assembly according to claim 1, characterized in that: An included angle between a center line of the intake valve guide and a center line of the intake flow passage is A1, and satisfies: 40°≤A1≤45°.

3. The cylinder head assembly according to claim 2, characterized in that: Satisfies: 42.5°≤A1≤43.5°.

4. The cylinder head assembly according to claim 1, wherein: The intake flow passage is connected to a side of the intake throat away from the exhaust port; An included angle A2 between a tangent line of the guide surface at one end connected to the air inlet throat and a line parallel to the bottom surface of the exhaust port satisfies the following conditions: 150°≤A2≤165°.

5. The cylinder head assembly according to claim 4, characterized in that: Satisfies: 155°≤A2≤160°.

6. The cylinder head assembly according to any one of claims 1 to 5, characterized in that: There are two air inlets and two exhaust outlets, which are distributed in a one-to-one correspondence; There are two air inlet pipes connected to the two air inlets in a one-to-one correspondence, and the two air inlet pipes extend obliquely from a direction close to the air inlet toward a direction away from each other.

7. The cylinder head assembly according to claim 6, characterized in that The included angle between the extension directions of the two air intake pipes is A3, and satisfies: 14°≤A3≤20°.

8. The cylinder head assembly according to claim 7, wherein: Meets: 14°≤A3≤18°.

9. The cylinder head assembly according to claim 6, wherein: The air inlets and the corresponding air outlets are spaced apart along a first direction, and the two air inlets are spaced apart along a second direction, and the second direction intersects the first direction; Wherein, air-guiding side walls are formed at both side edges of the cylinder cover in the second direction, and the two air-guiding side walls extend obliquely toward each other along the direction from the air inlet to the exhaust port.

10. The cylinder head assembly according to claim 9, characterized in that The included angle between the extension directions of the two air-guiding side walls is A4, and satisfies: 10°≤A4≤20°.

11. The cylinder head assembly according to claim 10, wherein: Meet the requirements: 13°≤A4≤17°.

12. The cylinder head assembly according to claim 9, wherein: An included angle between the air guide side wall and the extending direction of the air intake pipe on the same side is A5, and satisfies: 10°≤A5≤20°.

13. The cylinder head assembly according to claim 12, wherein: Meets: 13°≤A5≤17°.

14. The cylinder head assembly according to any one of claims 1 to 5, characterized in that: The center line of the intake throat coincides with the center line of the intake valve guide.

15. A vehicle, characterized in that: A cylinder head assembly comprising the cylinder head assembly according to any one of claims 1 to 14.

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