Engine cylinder cover, engine and vehicle
By designing staggered intake ports and valves on the engine cylinder head, combined with rocker arm-driven differentiated opening, an in-cylinder vortex is created, solving the problem of incomplete combustion in large-bore engines and achieving the effect of reducing gas consumption and emissions.
Patent Information
- Application Number
- CN202423312148.7
- Authority / Receiving Office
- CN · China
- Patent Type
- Utility models(China)
- Current Assignee / Owner
- Filing Date
- 2024-12-31
- Publication Date
- 2025-11-18
- Estimated Expiration
- 2034-12-31
AI Technical Summary
Large-bore engines have difficulty generating circumferential vortices in the cylinder during combustion, resulting in a long duration of the later stages of combustion, incomplete combustion, high gas consumption and emissions, and an inability to meet the requirements for reducing gas consumption and emissions.
Design an engine cylinder head that employs a staggered first and second intake manifold, combined with a differentially opened first and second valve, driven by a first and second rocker arm to achieve asymmetrical airflow supply, weakening and canceling vortex components, constructing a vortex based on strong tumble flow, and promoting in-cylinder combustion.
By using a staggered intake manifold and valve design, in-cylinder combustion efficiency is improved, and engine gas consumption and emissions are reduced.
Smart Images
Figure CN223562926U_ABST
Abstract
Description
TECHNICAL FIELD
[0001] The present application relates to the technical field of engines, in particular to an engine cylinder head, an engine and a vehicle. BACKGROUND
[0002] Rolling flow is beneficial to improve the center turbulent kinetic energy in the cylinder, accelerate the development speed of the initial fire core, and improve the thermal efficiency of the engine. For large-bore engines (referring to engines with a cylinder diameter exceeding 150mm), parallel air ducts are used to construct rolling flow, but it is difficult to generate circumferential vortex flow in the cylinder. As the combustion process develops, the rolling flow effect gradually weakens, and the flame develops slowly in the later stage, resulting in a long combustion duration and incomplete combustion, high gas consumption and high emissions, which do not meet the needs of modern engines to reduce gas consumption and emissions.
[0003] Therefore, how to reduce the gas consumption and emissions of the engine has become a technical problem to be solved by those skilled in the art. CONTENT OF THE UTILITY MODEL
[0004] The present application provides an engine cylinder head to reduce the gas consumption and emissions of the engine. The present application also provides an engine and a vehicle.
[0005] In order to achieve the above-mentioned purpose, the present application provides an engine cylinder head, comprising:
[0006] The cylinder head body is a flat-top cylinder head;
[0007] The first intake port and the second intake port are both rolling flow air ducts, and are located on the first side of the cylinder head front-rear end direction connecting line of the cylinder head body and are distributed in a staggered manner in a direction perpendicular to the cylinder head front-rear end direction connecting line;
[0008] The first valve and the second valve are arranged perpendicular to the bottom surface of the cylinder head body, and the first valve and the second valve are distributed in a staggered manner in a direction perpendicular to the cylinder head front-rear end direction connecting line;
[0009] The first rocker arm and the second rocker arm are both rotatable around a rocker arm shaft, the axis of the rocker arm shaft is parallel to the cylinder head front-rear end direction connecting line, the first rocker arm and the second rocker arm each have a driving end and a driven end located on both sides of the rocker arm shaft, the driving end of the first rocker arm and the driving end of the second rocker arm are matched with a camshaft, the first distance a1 between the driving end of the first rocker arm and the second rocker arm is equal to the distance between the first valve and the rocker arm shaft, the second distance b2 between the driven end of the first rocker arm and the rocker arm shaft is adapted to the distance between the first valve and the rocker arm shaft, the driven end of the second rocker arm is connected with the second valve, and the third distance b1 between the driven end of the second rocker arm and the rocker arm shaft is adapted to the distance between the second valve and the rocker arm shaft.
[0010] Preferably, in the above engine cylinder head, the first valve is closer to the line connecting the front and rear ends of the cylinder head than the second valve, the second distance b2 is greater than the third distance b1,
[0011] The first rocker arm ratio b2 / a1 of the second distance b2 to the first distance a1 is greater than the second rocker arm ratio b1 / a1 of the third distance b1 to the first distance a1,
[0012] The first rocker arm ratio b2 / a1 is less than 1.7, and the second rocker arm ratio b1 / a1 is greater than 1.2.
[0013] Preferably, in the above engine cylinder head, the angle between the straight line on which the first valve and the second valve are located and the line connecting the front and rear ends of the cylinder head is θ, and 5°<θ<20°.
[0014] Preferably, in the above engine cylinder head, the maximum lift H1 of the first valve and the maximum lift H2 of the second valve satisfy 0.5H1<H2<H1.
[0015] Preferably, in the above engine cylinder head, the first rocker arm and the second rocker arm share the driving end.
[0016] Preferably, in the above engine cylinder head, the first valve and the second valve are opened and closed simultaneously.
[0017] Preferably, in the above engine cylinder head, the first valve and the second valve are parallel.
[0018] An engine comprising an engine cylinder head, the engine cylinder head being the engine cylinder head described in any one of the above aspects.
[0019] Preferably, in the above engine, the camshaft driving the first rocker arm and the second rocker arm of the engine cylinder head is a top camshaft.
[0020] A vehicle comprising an engine, the engine being the engine described in any one of the above aspects.
[0021] The scheme discloses an engine cylinder cover, which has a flat top structure surrounding a combustion chamber with pistons and cylinders of an engine, a first intake port and a second intake port are arranged on a first side of a cylinder cover front-rear direction line of the flat top structure, the first intake port and the second intake port are distributed in a direction perpendicular to the cylinder cover front-rear direction line, and a first valve of the first intake port and a second valve of the second intake port are distributed in the direction perpendicular to the cylinder cover front-rear direction line. The first intake port and the second intake port are distributed in the direction perpendicular to the cylinder cover front-rear direction line, so that the airflow supplied into the cylinder through the first intake port and the second intake port is asymmetric, the counteraction between the vortex components formed by the first intake port and the second intake port is weakened, and the vortex is generated in the cylinder; the first valve and the second valve distributed in a staggered manner are driven by a first rocker arm and a second rocker arm matched with the first valve and the second valve, the differential opening of the first valve and the second valve is realized, the lift of the first valve is different from the lift of the second valve, the opening degree of the first intake port is different from the opening degree of the second intake port, the air intake amount of the first intake port is different from the air intake amount of the second intake port, the tumble flow capacity of the first intake port and the second intake port is asymmetric, the counteraction between the vortex components formed by the first intake port and the second intake port is weakened, the vortex is constructed on the basis of strong tumble flow, the combustion in the cylinder is accelerated, and the emission and gas consumption of the engine are reduced.
[0022] The scheme also discloses an engine, which comprises the engine cylinder cover.
[0023] The scheme also discloses a vehicle, which comprises the engine. BRIEF DESCRIPTION OF DRAWINGS
[0024] In order to more clearly illustrate the technical solutions in the embodiments of the present application or the prior art, the drawings needed in the embodiments or the prior art description will be briefly introduced below. Obviously, the drawings in the following description are only some examples or embodiments of the present application, and for those skilled in the art, other drawings can be obtained without creative labor on the basis of the provided drawings, and the present application can also be applied to other similar scenarios on the basis of the provided drawings. Unless it is obvious from the language environment or otherwise stated, the same reference numerals in the drawings represent the same structure or operation.
[0025] Figure 1 is a structural schematic diagram of the engine cylinder cover of the present application;
[0026] Figure 2 is a top view of the engine cylinder cover of the present application;
[0027] Figure 3 is a structural schematic diagram of a common driving end of first and second rocker arms of an engine cylinder head of the present application;
[0028] Figure 4 is a valve lift curve of first and second valves of an engine cylinder head of the present application.
[0029] The accompanying drawings are described as follows:
[0030] 1-cylinder head body; 2-first intake port; 3-second intake port; 4-first valve; 5-second valve; 6-first rocker arm; 7-second rocker arm; 8-cylinder head front-rear direction connecting line; 9-camshaft. DETAILED DESCRIPTION
[0031] The present application will be further described below in conjunction with the drawings and embodiments. It can be understood that the specific embodiments described herein are only used to explain the related application, but not to limit the application. The described embodiments are only a part of the embodiments of the present application, but not all the embodiments. Based on the embodiments in the present application, all other embodiments obtained by those skilled in the art without making creative efforts fall within the scope of protection of the present application.
[0032] It should be noted that, for the convenience of description, only the parts related to the application are shown in the drawings. The embodiments in the present application and the features in the embodiments can be combined with each other arbitrarily without conflict, as long as the combined technical features are not contradictory. All the feasible feature combinations are the technical contents explicitly described herein. Any one of the multiple features in the same sentence can be applied independently, and does not have to be applied together with other features.
[0033] As shown in the present application and claims, unless the context clearly indicates otherwise, the words “one”, “a”, “an”, and / or “the” do not specifically refer to the singular, but also include the plural. Generally, the terms “comprise” and “include” only indicate the inclusion of the steps and elements explicitly identified, and these steps and elements do not constitute an exclusive list, and the method or device can also include other steps or elements. The element defined by the phrase “comprising a” does not exclude the presence of additional identical elements in the process, method, product or device comprising the element.
[0034] In the description of the embodiments of the present application, unless otherwise specified, " / " represents the meaning of or, for example, A / B can represent A or B; "and / or" herein is only a description of the relationship between the associated objects, which means that there can be three relationships, for example, A and / or B, which can represent the existence of A alone, the existence of A and B together, and the existence of B alone. In addition, in the description of the embodiments of the present application, "multiple" means two or more than two.
[0035] In the related art, two intake ports of a cylinder are usually arranged in parallel, and the intake ports are tumble flow ports. Although the tumble flow ports are helpful to form tumble flow in the cylinder, the two intake ports are symmetrically distributed about the main axis of the cylinder, which causes the vortex components formed by the two intake ports to cancel each other out, and it is extremely difficult to generate vortex flow in the cylinder.
[0036] Tumble flow can drive airflow to rotate along the direction perpendicular to the axis of the cylinder, and vortex flow can drive airflow close to the cylinder wall to rotate around the axis of the cylinder. Properly increasing the vortex flow can increase the movement intensity of the gas around the cylinder wall, promote the combustion of natural gas around the cylinder wall, increase the combustion speed in the later stage of combustion, make the combustion more sufficient, and achieve the purpose of reducing emissions and improving thermal efficiency.
[0037] As shown in Figures 1-4 The engine cylinder head disclosed by the present scheme has a flat top structure surrounding a combustion chamber with pistons and cylinders of an engine, and a first side of a cylinder head front-rear direction connecting line 8 of the flat top structure is provided with a first intake port 2 and a second intake port 3.
[0038] The first intake port 2 and the second intake port 3 are tumble flow ports, and the tumble flow ports are composed of a flow guiding section and a flow guiding section connected in sequence in the intake direction. The flow guiding section is arranged obliquely downward, and the flow guiding section is arranged at an angle of less than 90° with the bottom surface of the engine cylinder head.
[0039] The first intake port 2 and the second intake port 3 are distributed in a staggered manner in a direction perpendicular to the cylinder head front-rear direction connecting line 8; a first valve 4 is arranged on the first intake port 2, and a second valve 5 is arranged on the second intake port 3; the first valve 4 and the second valve 5 are distributed in a staggered manner in a direction perpendicular to the cylinder head front-rear direction connecting line 8.
[0040] The first valve 4 is lifted or pressed by a first rocker arm 6, and the second valve 5 is lifted or pressed by a second rocker arm 7. When the first rocker arm 6 drives the first valve 4 to press down, the first intake port 2 is opened, and when the first rocker arm 6 drives the first valve 4 to lift up, the first intake port 2 is closed. When the second rocker arm 7 drives the second valve 5 to press down, the second intake port 3 is opened, and when the second rocker arm 7 drives the second valve 5 to lift up, the second intake port 3 is closed.
[0041] The engine cylinder head disclosed in the scheme, the first intake port 2 and the second intake port 3 are distributed in the direction perpendicular to the front and rear end direction connection line 8, so that the air flow supplied through the first intake port 2 and the second intake port 3 is asymmetric, to weaken the offset between the vortex components formed by the first intake port 2 and the second intake port 3, and to generate vortex in the cylinder.
[0042] The first valve 4 and the second valve 5 are distributed in the direction perpendicular to the front and rear end direction connection line 8, and the first rocker arm 6 and the second rocker arm 7 need to adapt to the position change of the first valve 4 and the second valve 5.
[0043] The first rocker arm 6 and the second rocker arm 7 are rotated around the rocker arm shaft, the parts of the first rocker arm 6 located at both ends of the rocker arm shaft are the driving end and the driven end of the first rocker arm 6 respectively, and the parts of the second rocker arm 7 located at both ends of the rocker arm shaft are the driving end and the driven end of the second rocker arm 7 respectively, the driving end of the first rocker arm 6 and the driving end of the second rocker arm 7 cooperate with the camshaft 9, the first distance a1 between the driving end of the first rocker arm 6 and the second distance b2 between the driven end of the first rocker arm 6 and the rocker arm shaft are adapted to the distance between the first valve 4 and the rocker arm shaft, the driven end of the first rocker arm 6 is connected with the first valve 4, the second distance b2 between the driven end of the first rocker arm 6 and the rocker arm shaft is adapted to the distance between the first valve 4 and the rocker arm shaft, the driven end of the second rocker arm 7 is connected with the second valve 5, and the third distance b1 between the driven end of the second rocker arm 7 and the rocker arm shaft is adapted to the distance between the second valve 5 and the rocker arm shaft. Figure 1 And 2 As shown in the figure, the distance between the first valve 4 and the front and rear end direction connection line 8 of the cylinder head is close to the second valve 5, that is, the distance between the first valve 4 and the rocker arm shaft is greater than the distance between the second valve 5 and the rocker arm shaft, the second distance b2 between the driven end of the first rocker arm 6 and the rocker arm shaft is greater than the third distance b1 between the driven end of the second rocker arm 7 and the rocker arm shaft, so that the first rocker arm ratio of the first rocker arm 6 is greater than the second rocker arm ratio of the second rocker arm 7. It should be noted here that the first rocker arm ratio is the ratio of the second distance b2 between the driven end of the first rocker arm 6 and the rocker arm shaft to the first distance a1, and the second rocker arm ratio is the ratio of the third distance b1 between the driven end of the second rocker arm 7 and the rocker arm shaft to the first distance a1.
[0044] The first rocker arm 6 and the second rocker arm 7 drive the first valve 4 and the second valve 5 to move synchronously, but the lift of the first valve 4 and the second valve 5 is different, realizing the differential opening of the first valve 4 and the second valve 5, the lift of the first valve 4 is different from the lift of the second valve 5, so that the opening of the first intake port 2 is different from the opening of the second intake port 3, and then the intake amount of the first intake port 2 is different from the intake amount of the second intake port 3, the tumble flow capacity of the first intake port 2 and the second intake port 3 is asymmetric, to weaken the offset between the vortex components formed by the first intake port 2 and the second intake port 3, to build vortex on the basis of strong tumble flow, to accelerate the combustion in the cylinder, and to reduce the emission and gas consumption of the engine.
[0045] In some embodiments, the first rocker ratio b2 / a1 is greater than the second rocker ratio b1 / a1, where the first rocker ratio b2 / a1 < 1.7 and the second rocker ratio b1 / a1 > 1.2. That is, the maximum value of the first rocker ratio b2 / a1 does not exceed 1.7, and the minimum value of the second rocker ratio b1 / a1 is not less than 1.2.
[0046] In some embodiments, the angle θ between the straight line where the first valve 4 and the second valve 5 are located and the connecting line 8 of the front and rear ends of the cylinder head is 5° < θ < 20°. The larger θ is, the easier it is to obtain a larger movement height difference and better form a vortex in the cylinder.
[0047] The maximum lift H1 of the first valve 4 and the maximum lift H2 of the second valve 5 satisfy 0.5H1 < H2 < H1. When the first valve 4 and the second valve 5 are opened differently, a vortex is constructed on the basis of a strong tumble flow, accelerating the combustion in the cylinder and reducing the emissions of the engine.
[0048] In some embodiments, as Figure 2 shown, the first rocker 6 and the second rocker 7 are two separate rockers. That is, the first rocker 6 has an active end and a passive end, the second rocker 7 has an active end and a passive end. The active end of the first rocker 6 is engaged with the camshaft 9, the active end of the second rocker 7 is engaged with the camshaft 9. The first rocker 6 and the second rocker 7 are connected to the same camshaft 9. The passive end of the first rocker 6 is connected to the first valve 4, and the passive end of the second rocker 7 is connected to the second valve 5. The camshaft 9 drives the first rocker 6 and the second rocker 7 to move synchronously, and the first rocker 6 and the second rocker 7 drive the first valve 4 and the second valve 5 to move synchronously, realizing the differential opening of the first valve 4 and the second valve 5.
[0049] In some embodiments, the first rocker 6 and the second rocker 7 share an active end, and the first rocker 6 and the second rocker 7 have their respective passive ends. As Figure 3 shown, the first rocker 6 and the second rocker 7 are integrally in a Y shape, and the lengths of the two branches of the Y-shaped structure are different. The camshaft 9 drives the common active end of the first rocker 6 and the second rocker 7 to move,带动 the respective passive ends of the first rocker 6 and the second rocker 7 to move synchronously, realizing the differential opening of the first valve 4 and the second valve 5.
[0050] The greater the difference in the intake air volume between the first valve 4 and the second valve 5 and the greater the spacing of the misaligned distribution, the easier it is to construct a vortex.
[0051] In some embodiments, the first valve 4 and the second valve 5 are parallel, and the first valve 4 and the second valve 5 can also be misaligned in the direction perpendicular to the connecting line 8 of the front and rear ends of the cylinder head.
[0052] In this solution, the first valve 4 and the second valve 5 are opened and closed simultaneously. AsFigure 4 The solid line and the dashed line in the valve lift curve represent the working processes of the first valve and the second valve in the intake stage, respectively. In the intake stage, the first valve and the second valve are opened simultaneously, and the lift of the first valve is always greater than that of the second valve during the opening process of the valve, and the maximum lift of the first valve is greater than that of the second valve; during the closing process of the valve, the lift of the first valve is also always greater than that of the second valve, and finally the two valves are closed simultaneously.
[0053] The engine is also disclosed in the present application, and the engine is the engine as described in any one of the above embodiments.
[0054] The engine has the technical effects as described above, and the vehicle with the engine also has the same technical effects.
[0055] The camshaft 9 driving the first rocker arm 6 and the second rocker arm 7 of the engine cylinder head is an overhead camshaft. The design of the overhead camshaft can shorten the distance between the camshaft and the valve, simplify the transmission mechanism from the camshaft 9 to the valve, make the engine structure more compact, and improve the transmission efficiency.
[0056] The vehicle is also disclosed in the present application, and the vehicle is the vehicle as described in any one of the above embodiments.
[0057] The vehicle has the technical effects as described above.
[0058] The above description is merely preferred embodiments of the present application and a description of the principles of the technology used, and is not intended to limit the present application. The present application can have various changes and modifications for those skilled in the art. The scope of the application involved in the present application is not limited to the technical solutions formed by the specific combinations of the technical features described above, and should also cover other technical solutions formed by any combination of the above technical features or equivalent features without departing from the above application concept. For example, the technical solutions formed by replacing the above features with the technical features disclosed in the present application (but not limited to) having similar functions.
Claims
1. An engine cylinder head characterized by, The cylinder head body (1) is a flat-top cylinder head. The first intake port (2) and the second intake port (3) are both tumble flow ports, and are located on the first side of the cylinder head front-rear direction connecting line (8) of the cylinder head body (1) and are distributed in a staggered manner in a direction perpendicular to the cylinder head front-rear direction connecting line (8). The first valve (4) and the second valve (5) are arranged perpendicular to the bottom surface of the cylinder head body (1), and the first valve (4) and the second valve (5) are distributed in a staggered manner in a direction perpendicular to the cylinder head front-rear direction connecting line (8). The first rocker arm (6) and the second rocker arm (7) are both rotatable around a rocker arm shaft, and the axis of the rocker arm shaft is parallel to the cylinder head front-rear direction connecting line (8). The first rocker arm (6) and the second rocker arm (7) each have a driving end and a driven end located on both sides of the rocker arm shaft. The driving end of the first rocker arm (6) and the driving end of the second rocker arm (7) are matched with a camshaft (9). The first distance a1 between the driving end of the first rocker arm (6) and the driving end of the second rocker arm (7) is equal to the distance between the rocker arm and the camshaft (9). The driven end of the first rocker arm (6) is connected to the first valve (4), and the second distance b2 between the driven end of the first rocker arm (6) and the rocker arm shaft is adapted to the distance between the first valve (4) and the rocker arm shaft. The driven end of the second rocker arm (7) is connected to the second valve (5), and the third distance b1 between the driven end of the second rocker arm (7) and the rocker arm shaft is adapted to the distance between the second valve (5) and the rocker arm shaft. The first valve (4) is closer to the cylinder head front-rear direction connecting line (8) than the second valve (5), and the second distance b2 is greater than the third distance b1.
2. The engine cylinder head of claim 1, wherein, The first rocker arm ratio b2 / a1 is greater than the second rocker arm ratio b1 / a1. The first rocker arm ratio b2 / a1 is less than 1.7, and the second rocker arm ratio b1 / a1 is greater than 1.
2. The angle between the straight line on which the first valve (4) and the second valve (5) are located and the cylinder head front-rear direction connecting line (8) is θ, and 5°<θ<20°.
3. The engine cylinder head of claim 2, wherein, The highest lift H1 of the first valve (4) and the highest lift H2 of the second valve (5) satisfy 0.5H1<H2<H1.
4. The engine cylinder head according to any one of claims 1-3, characterized in that, The first rocker arm and the second rocker arm (7) share the driving end.
5. The engine cylinder head of claim 1, wherein, The first valve (4) and the second valve (5) are opened and closed simultaneously.
6. The engine cylinder head of claim 1, wherein, The first valve (4) and the second valve (5) are parallel.
7. The engine cylinder head of claim 1, wherein, The engine cylinder head is the engine cylinder head of any one of claims 1-7.
8. An engine characterized by, The camshaft (9) driving the movement of the first rocker arm (6) and the second rocker arm (7) of the engine cylinder head is a top-mounted camshaft (9).
9. The engine of claim 8, wherein, The engine is the engine of any one of claims 8-9.
10. A vehicle characterized by comprising: