Engine and vehicle

Abstract

The application relates to the engine technical field, and discloses an engine and a vehicle.The engine comprises a cylinder cover and a rocker arm, the cylinder cover is provided with a valve hole, a mounting hole and a main oil passage located between the valve hole and the mounting hole and communicated with the mounting hole, the rocker arm is movably arranged on the cylinder cover, the rocker arm comprises a rocker arm body and first and second arms located on two sides of the rocker arm body, the first arm is opposite to the valve hole, the second arm is opposite to the mounting hole, and a recess for avoiding the rocker arm is arranged on a region of an outer wall surface of the main oil passage facing the rocker arm, and the recess is recessed towards an inner hole of the main oil passage. Thus, contact between the main oil passage and the rocker arm can be avoided, the cylinder cover does not need to be lifted, the valve length is not needed to be lengthened, the mass of the cylinder cover and the valve can be reduced to meet the light weight requirement, the longitudinal height of the engine can be reduced, the arrangement difficulty of the engine can be reduced, and the cost of the engine can be reduced.

Description

Technical Field

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

[0002] In related technologies, the engine uses a rocker arm in conjunction with a hydraulic tappet to selectively open and close the intake and exhaust valves. The rocker arm needs to swing back and forth with the hydraulic tappet as the support point.

[0003] However, in order to ensure that the rocker arm does not hit the hydraulic tappet mounting holes of the cylinder head during reciprocating swing, it is necessary to raise the height of the camshaft center and lengthen the valves, resulting in a higher cylinder head height and increased cylinder head weight. This is not conducive to reducing the manufacturing cost of the cylinder head and thus the engine manufacturing cost. At the same time, the higher cylinder head height increases the overall engine height, resulting in higher requirements for the longitudinal mounting arrangement of the engine and making mounting arrangement difficult. Utility Model Content

[0004] This invention aims to solve at least one of the technical problems existing in the prior art. Therefore, one objective of this invention is to provide an engine in which the rocker arm does not collide with the mounting hole and main oil passage during its swing, and without requiring the camshaft center height to be raised or the valve length to be increased, thereby reducing engine cost, weight, and space occupation, and simplifying layout.

[0005] This application further proposes a vehicle employing the aforementioned engine.

[0006] In a first aspect, this application provides an engine, including: a cylinder head and a rocker arm, the cylinder head having a valve hole, a mounting hole, and a main oil passage located between the valve hole and the mounting hole and communicating with the mounting hole, the rocker arm being movably disposed on the cylinder head, the rocker arm including a rocker arm body and a first arm and a second arm located on both sides of the rocker arm body, the first arm being opposite to the valve hole, the second arm being opposite to the mounting hole, and a recess for avoiding the rocker arm being provided on the outer wall surface of the main oil passage facing the area of ​​the rocker arm, the recess being recessed towards the inner hole of the main oil passage.

[0007] According to the engine of the present application embodiment, by providing a recess on the outer wall surface of the lower contour of the main oil passage facing the rocker arm body, the rocker arm can be avoided by the recess, thus preventing contact between the main oil passage, mounting hole and rocker arm. Therefore, it is not necessary to raise the cylinder head and extend the valve length, which can reduce the mass of the cylinder head and valve to meet the requirements of lightweighting. At the same time, the longitudinal height of the engine can be reduced, the layout difficulty of the engine can be reduced, and the cost of the engine can be reduced.

[0008] According to some embodiments of this application, the cross-sectional profile of the recess is arc-shaped.

[0009] According to some embodiments of this application, the radius of the concave surface is smaller than the radius of the outer contour of the second arm facing the main oil passage, and the centers of both are located on the side of the rocker arm body facing the main oil passage.

[0010] According to some embodiments of this application, the minimum distance D1 between the recess and the inner wall of the main oil passage is ≥2mm.

[0011] According to some embodiments of this application, the engine further includes: a valve and a hydraulic tappet, the valve being movably disposed in the valve hole, the first arm abutting against the valve, the hydraulic tappet being mounted in the mounting hole, the second arm abutting against the hydraulic tappet, and the width D2 of the second arm and the dimension D3 of the recess in the width direction of the second arm satisfying: D2≤D3.

[0012] According to some embodiments of this application, the engine further includes: a camshaft, a cam on the camshaft contacting the rocker arm to drive the first arm to push the valve, the angle between the axis of the valve and the axis of the hydraulic tappet is a1, and the angle between the axis of the valve and the line connecting the center of the camshaft and the center of the rocker arm body is a2, and a2≤a1.

[0013] According to some embodiments of this application, 0.2a1≤a2≤0.7a1.

[0014] According to some embodiments of this application, the mounting hole is provided with an oil drain section, the hydraulic tappet has an oil inlet and an oil drain hole, the main oil passage is connected to the oil inlet, the oil drain section is connected to the oil drain hole of the hydraulic tappet, and the included angle a3 between the oil drain section and the bottom surface of the mounting hole is greater than or equal to 90°.

[0015] According to some embodiments of this application, when the valve is closed, the distance D4 between the outer contour of the rocker arm body facing the main oil passage and the outer contour of the main oil passage is ≥1mm.

[0016] Secondly, this application provides a vehicle including the engine described in the above embodiments.

[0017] Additional aspects and advantages of this invention will be set forth in part in the description which follows, and in part will be obvious from the description, or may be learned by practice of the invention. Attached Figure Description

[0018] The above and / or additional aspects and advantages of this utility model will become apparent and readily understood from the description of the embodiments taken in conjunction with the following drawings, in which: Figure 1This is a schematic diagram of a cylinder head according to an embodiment of this application; Figure 2 This is a schematic diagram of the fit between the cylinder head, rocker arm, camshaft, valve and hydraulic tappet according to an embodiment of this application; Figure 3 yes Figure 2 The center circle shows a magnified view of a portion of area A; Figure 4 This is a top view of the cylinder head and rocker arm according to an embodiment of this application; Figure 5 This is a top view of a cylinder head according to an embodiment of this application.

[0019] Figure label: Cylinder head 10, valve hole 11, mounting hole 12, oil drain 121, main oil passage 13, recess 131 Rocker arm 20, rocker arm body 21, first arm 22, second arm 23, outer contour 231 of the second arm facing the main oil passage. Camshaft 30, valves 40, hydraulic tappets 50 The minimum distance D1 between the recess and the inner wall of the main oil passage; the width D2 of the second arm; the dimension D3 of the recess in the width direction of the second arm; and the distance D4 between the outer contour of the rocker arm body facing the main oil passage and the outer contour of the main oil passage. The angle between the valve axis and the hydraulic tappet axis is a1, the angle between the valve axis and L1 is a2, and the angle between the drain section and the bottom surface of the mounting hole is a3. Detailed Implementation

[0020] To make the objectives, technical solutions, and advantages of the embodiments of this application clearer, the technical solutions of the embodiments of this application will be clearly described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of this application, not all embodiments. Based on the embodiments of this application, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of this application.

[0021] Unless otherwise defined, all technical and scientific terms used in this application have the same meaning as commonly understood by one of ordinary skill in the art to which this application pertains; the terminology used in the description of this application is for the purpose of describing particular embodiments only and is not intended to limit the application; the terms "comprising" and "having," and any variations thereof, in the description, claims, and accompanying drawings of this application are intended to cover non-exclusive inclusion. The terms "first," "second," etc., in the description, claims, or accompanying drawings of this application are used to distinguish different objects, not to describe a specific order or hierarchy.

[0022] In this application, the reference to "embodiment" means that a particular feature, structure, or characteristic described in connection with an embodiment may be included in at least one embodiment of this application. The appearance of this phrase in various places in the specification does not necessarily refer to the same embodiment, nor is it a separate or alternative embodiment that is mutually exclusive with other embodiments.

[0023] In the description of this application, it should be noted that, unless otherwise expressly specified and limited, the terms "installation," "connection," "linking," and "attachment" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; they can refer to a direct connection or an indirect connection through an intermediate medium; and they can refer to the internal communication between two components. Those skilled in the art can understand the specific meaning of the above terms in this application according to the specific circumstances.

[0024] In this application, the term "and / or" is merely a description of the relationship between related objects, indicating that three relationships can exist. For example, A and / or B can represent: A existing alone, A and B existing simultaneously, or B existing alone. Additionally, in this application, the character " / " generally indicates that the preceding and following related objects have an "or" relationship.

[0025] In the embodiments of this application, the same reference numerals denote the same components, and for the sake of brevity, detailed descriptions of the same components are omitted in different embodiments. It should be understood that the thickness, length, width, and other dimensions of various components in the embodiments of this application shown in the accompanying drawings, as well as the overall thickness, length, width, and other dimensions of the integrated device, are merely illustrative and should not constitute any limitation on this application.

[0026] In the description of this utility model, it should be understood that the terms "center", "longitudinal", "transverse", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", "axial", "radial", "circumferential", etc., indicating the orientation or positional relationship are based on the orientation or positional relationship shown in the accompanying drawings, and are only for the convenience of describing this utility model and simplifying the description, and are not intended to indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of this utility model.

[0027] In the description of this utility model, the first feature being "above" or "below" the second feature may include the first and second features being in direct contact, or it may include the first and second features not being in direct contact but being in contact through another feature between them.

[0028] In the description of this utility model, the terms "above", "over" and "on top" for the first feature and the second feature include the first feature being directly above or diagonally above the second feature, or simply indicate that the first feature is at a higher horizontal level than the second feature.

[0029] In this application, "multiple" means two or more (including two).

[0030] In related technologies, the engine uses a rocker arm in conjunction with a hydraulic tappet to selectively open and close the intake and exhaust valves. The rocker arm needs to swing back and forth with the hydraulic tappet as the support point.

[0031] However, in order to ensure that the rocker arm does not hit the hydraulic tappet mounting holes of the cylinder head during reciprocating swing, it is necessary to raise the height of the camshaft center and lengthen the valve length, resulting in a higher cylinder head height, increased cylinder head weight, which is not conducive to reducing the manufacturing cost of the cylinder head and the engine. At the same time, the higher cylinder head height leads to an increase in the overall engine height, resulting in higher requirements for engine mounting (especially longitudinal mounting), making mounting difficult.

[0032] Based on this, this application proposes an engine that, without increasing the cylinder head height or extending the valve (valve stem) length, ensures that the rocker arm will not touch the hydraulic tappet mounting hole during the swinging process. This not only reduces the center height behind the cylinder head camshaft, but also reduces the cylinder head height and valve length, thereby achieving a lightweight design, reducing the engine's space occupation, lowering costs, and simplifying layout.

[0033] The following is for reference. Figures 1-5 This invention describes an engine and a vehicle according to embodiments of the present invention.

[0034] like Figure 1 , Figure 2 and Figure 3 As shown, this application provides an engine, including: a cylinder head 10 and a rocker arm 20. The cylinder head 10 has a valve hole 11, a mounting hole 12, and a main oil passage 13 located between the valve hole 11 and the mounting hole 12 and communicating with the mounting hole 12. The rocker arm 20 is movably disposed on the cylinder head 10. The rocker arm 20 includes a rocker arm body 21 and a first arm 22 and a second arm 23 located on both sides of the rocker arm body 21. The first arm 22 is opposite to the valve hole 11, and the second arm 23 is opposite to the mounting hole 12. A recess 131 for avoiding the rocker arm 20 is provided on the outer wall surface of the main oil passage 13 facing the area of ​​the rocker arm 20. The recess 131 is recessed towards the inner hole of the main oil passage 13.

[0035] Specifically, the cylinder head 10 is provided with valve holes 11, mounting holes 12, and camshaft mounting holes 12. The valve guide is interference-fitted into the valve hole 11, and the valve 40 passes through the valve guide. The valve 40 can be an intake valve or an exhaust valve, and the corresponding valve hole 11 can be an intake valve hole or an exhaust valve hole. The intake valve is set with the intake port on the cylinder head, and the exhaust valve is set with the exhaust port on the cylinder head. The valve 40 is used to selectively open and close the intake port and exhaust port on the cylinder head 10. The hydraulic tappet 50 is mounted in the mounting hole 12, and the camshaft 30 is mounted in the camshaft mounting hole 12. When the cam of the camshaft 30 rotates, it drives the rocker arm 20. The rocker arm 20 reciprocates with the hydraulic tappet 50 as the support point to control the opening and closing of the valve 40.

[0036] It should be noted that when the cam lobe of the camshaft 30 contacts the rocker arm 20, the valve 40 is in the open state. The force is directly and effectively transmitted to the rocker arm 20 and the valve 40 through the hydraulic tappet 50, overcoming the elastic force of the valve spring and opening the valve 40 smoothly and quickly until the valve 40 reaches its maximum lift. At this stage, the distance between the lower contour of the rocker arm body 21 (i.e., the contour surface of the rocker arm body 21 facing the main oil passage 13) and the outer contour of the main oil passage 13 is at or close to the minimum value in the reciprocating motion. In the prior art, in order to ensure that the rocker arm 20 does not collide with the main oil passage 13 at this stage, the length of the valve 40 is increased to increase the distance between the lower contour of the rocker arm body 21 and the outer contour of the main oil passage 13. However, this will increase the center height of the camshaft 30, which in turn will increase the height of the cylinder head 10, resulting in increased manufacturing costs of the valve 40 and cylinder head 10, and increased difficulty in engine layout (especially longitudinal layout).

[0037] Furthermore, this application provides a recess 131 on the outer wall of the main oil passage 13. The wall of the recess 131 is recessed away from the rocker arm 20, so that the distance between the lower contour of the rocker arm body 21 and the main oil passage 13 is larger, so that the probability of the rocker arm 20 hitting the main oil passage 13 during the swinging process is lower. Therefore, it is not necessary to raise the cylinder head 10 and extend the length of the valve 40, which can reduce the mass of the cylinder head 10 and the valve 40 to meet the requirements of lightweighting. At the same time, it can reduce the longitudinal height of the engine, reduce the difficulty of engine layout, and reduce the cost of the engine.

[0038] According to the engine of the present application embodiment, by providing a recess 131 on the outer wall surface of the main oil passage 13 facing the lower contour of the rocker arm body 21, the rocker arm 20 can be avoided by the recess 131, thus preventing contact between the main oil passage 13, the mounting hole 12 and the rocker arm 20. Therefore, it is not necessary to raise the cylinder head 10 and extend the length of the valve 40, which can reduce the mass of the cylinder head 10 and the valve 40 to meet the requirements of lightweighting. At the same time, the longitudinal height of the engine can be reduced, the layout difficulty of the engine can be reduced, and the cost of the engine can be reduced.

[0039] like Figure 3As shown, according to some embodiments of this application, the cross-sectional profile of the recess 131 is arc-shaped.

[0040] This makes the outline of the recess 131 smoother, which can prevent local protrusions on the wall of the recess 131, further reducing the probability of contact between the recess 131 and the rocker arm 20, reducing the wear of the rocker arm 20, extending the service life of the rocker arm 20, and improving the stability and reliability of the engine.

[0041] According to some embodiments of this application, the radius of the concave surface of the recess 131 is smaller than the radius of the outer contour 231 of the second arm 23 facing the main oil passage 13, and the centers of both are located on the side of the rocker arm body 21 facing the main oil passage 13.

[0042] Specifically, the radius of the concave wall of the recess 131 is smaller than the radius of the outer contour 231 of the second arm 23 facing the main oil passage 13 (that is, the cross-sectional contour of the area where the second arm 23 connects to the rocker arm body 21 facing the main oil passage 13 is arc-shaped, and the radius of the arc in this area is larger). This allows the valve 40 to have a larger lift, maximizing the valve 40 lift, thereby improving the valve 40 opening effect and ensuring intake and exhaust efficiency.

[0043] See Figure 3 As shown, according to some embodiments of this application, the minimum distance D1 between the recess 131 and the inner wall of the main oil passage 13 is ≥2mm.

[0044] Specifically, in order to prevent high-pressure oil in the main oil passage 13 from leaking out of the pit 131, the distance between the pit 131 and the inner wall of the main oil passage 13 should be no less than 2mm, such as 2mm, 3mm, 4mm, etc.

[0045] In this way, even if there are large machining deviations within the allowable error range during the casting process of the outer wall of the main oil passage 13 and / or the machining process of the main oil passage 13, the thickness of the dense aluminum alloy layer of the cylinder head 10 can still meet the requirements, so as to ensure the airtightness of the main oil passage 13 and the oil pressure stability of the high-pressure oil in the main oil passage 13, and prevent the high-pressure oil from seeping out from the pit 131.

[0046] like Figure 4 and Figure 5 As shown, according to some embodiments of this application, the engine further includes: a valve 40 and a hydraulic tappet 50. The valve 40 is movably disposed in the valve hole 11. A first arm 22 abuts against the valve 40. The hydraulic tappet 50 is mounted in the mounting hole 12. A second arm 23 abuts against the hydraulic tappet 50. The width D2 of the second arm 23 and the dimension D3 of the recess 131 in the width direction of the second arm 23 satisfy: D2≤D3.

[0047] Specifically, the rocker arm body 21 is movably mounted on the cylinder head 10, and the first arm 22 and the second arm 23 respectively abut against the hydraulic tappet 50 of the valve 40. The hydraulic tappet 50 can support the second arm 23 and, in conjunction with the internal oil pressure changes and the camshaft 30, realize the opening and closing of the valve 40.

[0048] In this application, the rocker arm 20 reciprocates with the hydraulic tappet 50 as the support point, causing the top plunger surface of the hydraulic tappet 50 to move in the cylinder arrangement direction with the contact surface of the rocker arm 20 (the surface of the second arm 23). The width D3 of the recess 131 is not less than the width dimension D2 of the second arm 23, which allows for sufficient clearance between the side wall of the second arm 23 and the recess 131 in the cylinder arrangement direction. This ensures the stability of the reciprocating motion of the rocker arm 20, prevents the second arm 23 from rubbing against the recess 131, avoids the rocker arm 20 from jamming, and improves the smoothness of the rocker arm 20's movement.

[0049] Combination Figure 2 and Figure 3 As shown, according to some embodiments of this application, the engine further includes: a camshaft 30, a cam on the camshaft 30 contacting a rocker arm 20 to drive a first arm 22 to push a valve 40, the angle between the axis of the valve 40 and the axis of the hydraulic tappet 50 is a1, and the angle between the axis of the valve 40 and the line connecting the center of the camshaft 30 and the center of the rocker arm body 21 is a2, and a2≤a1 is satisfied.

[0050] Specifically, the angle between valve 40 and hydraulic tappet 50 is a1, and the angle between the line L1 connecting the center of camshaft 30 and the center of rocker arm body 21 and the axis of valve 40 is a2, and a2 is greater than or equal to a1.

[0051] In this way, on the one hand, by arranging the valve 40 and the hydraulic tappet 50 at an angle, the height of the cylinder head 10 can be further reduced, thereby reducing the difficulty of layout, reducing costs, and meeting the requirements of lightweighting. On the other hand, the hydraulic tappet 50 and the valve 40 are arranged at an angle, which can easily generate lateral forces that cause wear on the valve 40 or valve guide. This makes the angle a2 less than or equal to the angle a1, which can match the position of the camshaft 30 center relative to the valve 40, thereby reducing lateral forces, reducing wear on the valve 40 and valve guide, and extending service life.

[0052] According to some embodiments of this application, 0.2a1≤a2≤0.7a1.

[0053] For example, a2 is 50°, and a1 can be 10°, 15°, 20°, 25°, 30°, 35°, etc., preferably 25°.

[0054] In this way, by setting the included angle a2 appropriately, the lateral force can be effectively reduced to an acceptable range, thereby reducing the probability of valve guide wear. At the same time, a more reasonable included angle a1 can reduce the height of the cylinder head 10 and the overall size of the engine. The reasonable setting of both a1 and a2 can ensure the reliability of engine operation.

[0055] like Figure 3 As shown, according to some embodiments of this application, an oil drain section 121 is provided on the mounting hole 12, the hydraulic tappet 50 has an oil inlet hole and an oil drain hole, the main oil passage 13 is connected to the oil inlet hole, the oil drain section 121 is connected to the oil drain hole of the hydraulic tappet 50, and the included angle α3 formed by the oil drain section 121 and the bottom surface of the mounting hole 12 is greater than or equal to 90°.

[0056] Specifically, the drain section 121 is located on the bottom surface of the hydraulic tappet mounting hole 12. Hydraulic oil can be supplied to the inlet hole from the main oil passage 13 and can be discharged from the hydraulic tappet 50 through the drain hole and returned through the drain section 121.

[0057] Therefore, by making the included angle a3 between the oil drain part 121 on the mounting hole 12 and the bottom surface of the mounting hole 12 greater than 90°, the machining burrs and flash at the intersection of the oil drain part 121 and the mounting hole 12 can be effectively reduced during the machining of the hydraulic tappet 50, and metal chips can be reduced, so as to ensure the cleanliness of the mounting hole 12 of the hydraulic tappet 50 and the cylinder head 10, and reduce the hidden dangers caused by poor cleanliness.

[0058] Combination Figure 2 and Figure 3 As shown, according to some embodiments of this application, when the valve 40 is in the closed state, the distance D4 between the outer contour of the rocker arm body 21 facing the main oil passage 13 and the outer contour of the main oil passage 13 is ≥1mm.

[0059] When the cam base circle of the camshaft 30 contacts the rocker arm 20, the valve 40 is in the closed state, the valve 40 mechanism has no load or very little load, the high pressure oil in the main oil passage 13 enters the hydraulic tappet 50 through the oil inlet hole, causing the plunger inside the hydraulic tappet 50 to move upward, so that the plunger and the rocker arm 20 contact tightly, so that the height of the hydraulic tappet 50 reaches the maximum or close to the maximum.

[0060] At this stage, the distance D4 between the lower contour of the rocker arm body 21 and the outer wall of the main oil passage 13 is at or near the maximum value during reciprocating motion. At this time, D4 ​​is not less than 1mm, and the corresponding D1 is not less than 2mm. This can effectively prevent the rocker arm body 21 from touching the outer contour of the main oil passage 13 and prevent the pit 131 from touching the second arm 23, thereby reducing the probability of the rocker arm 20 touching the main oil passage 13.

[0061] In summary, this application designs an arrangement structure for the camshaft 30, rocker arm 20, valve 40, and cylinder head 10, which ensures that the rocker arm 20 will not touch the mounting hole 12 and the main oil passage 13 during reciprocating swing. Correspondingly, there is no need to increase the height of the cylinder head 10 and the length of the valve 40, thereby reducing the center height of the camshaft 30, the height of the cylinder head 10, and the length of the valve 40. This effectively reduces the weight of the cylinder head 10 and the valve 40, effectively reduces the manufacturing cost of the cylinder head 10 and the valve 40, and achieves a lightweight design of the cylinder head 10 and the valve 40. This improves the engine performance, reduces the engine cost, and improves the engine's space utilization, especially the longitudinal space utilization. It can reduce the longitudinal height of the engine and reduce the difficulty of engine layout.

[0062] This application provides a vehicle, including the engine described in the above embodiments.

[0063] The vehicle according to the embodiments of this application, by employing the above-described engine, can reduce vehicle costs and improve vehicle driving stability.

[0064] The engine and other components and operation of the vehicle according to the embodiments of this utility model are known to those skilled in the art and will not be described in detail here.

[0065] In the description of this specification, the references to terms such as "one embodiment," "some embodiments," "illustrative embodiment," "example," "specific example," or "some examples," etc., indicate that a specific feature, structure, material, or characteristic described in connection with that embodiment or example is included in at least one embodiment or example of the present invention. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples.

[0066] Although embodiments of the present invention have been shown and described, those skilled in the art will understand that various changes, modifications, substitutions and alterations can be made to these embodiments without departing from the principles and spirit of the present invention, the scope of which is defined by the claims and their equivalents.

Claims

1. An engine, characterized in that, include: Cylinder head (10), the cylinder head (10) having valve holes (11), mounting holes (12), and a main oil passage (13) located between the valve holes (11) and the mounting holes (12) and communicating with the mounting holes (12). A rocker arm (20) is movably disposed on the cylinder head (10). The rocker arm (20) includes a rocker arm body (21) and a first arm (22) and a second arm (23) located on both sides of the rocker arm body (21). The first arm (22) is opposite to the valve hole (11), and the second arm (23) is opposite to the mounting hole (12). A recess (131) for avoiding the rocker arm (20) is provided on the outer wall surface of the main oil passage (13) facing the area of ​​the rocker arm (20). The recess (131) is recessed towards the inner hole of the main oil passage (13).

2. The engine according to claim 1, characterized in that, The cross-sectional profile of the pit (131) is arc-shaped.

3. The engine according to claim 2, characterized in that, The radius of the concave surface (131) is smaller than the radius of the outer contour (231) of the second arm (23) facing the main oil passage (13), and the center of both is located on the side of the rocker arm body (21) facing the main oil passage (13).

4. The engine according to claim 1, characterized in that, The minimum distance D1 between the pit (131) and the inner wall of the main oil passage (13) is ≥2mm.

5. The engine according to claim 1, characterized in that, The engine further includes a valve (40) and a hydraulic tappet (50). The valve (40) is movably disposed in the valve hole (11). The first arm (22) abuts against the valve (40). The hydraulic tappet (50) is installed in the mounting hole (12). The second arm (23) abuts against the hydraulic tappet (50). The width D2 of the second arm (23) and the dimension D3 of the recess (131) in the width direction of the second arm (23) satisfy: D2≤D3.

6. The engine according to claim 5, characterized in that, The engine further includes a camshaft (30), a cam on the camshaft (30) contacts the rocker arm (20) to drive the first arm (22) to push the valve (40), the angle between the axis of the valve (40) and the axis of the hydraulic tappet (50) is a1, the angle between the axis of the valve (40) and the line L1 connecting the center of the camshaft (30) and the center of the rocker arm body (21) is a2, and a2≤a1 is satisfied.

7. The engine according to claim 6, characterized in that, 0.2a1≤a2≤0.7a1.

8. The engine according to claim 5, characterized in that, An oil drain section (121) is provided on the mounting hole (12). The hydraulic tappet (50) has an oil inlet and an oil drain. The main oil passage (13) is connected to the oil inlet. The oil drain section (121) is connected to the oil drain of the hydraulic tappet (50). The included angle a3 between the oil drain section (121) and the bottom surface of the mounting hole (12) is greater than or equal to 90°.

9. The engine according to any one of claims 1-8, characterized in that, When the valve (40) is closed, the distance D4 between the outer contour of the rocker arm body (21) facing the main oil passage (13) and the outer contour of the main oil passage (13) is ≥1mm.

10. A vehicle, characterized in that, include: The engine according to any one of claims 1-9.

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