CN203783667U - Engine valve mechanism and engine - Google Patents

Abstract

The utility model provides an engine gas distribution mechanism, comprising an intake camshaft, an exhaust camshaft, an intake rocker arm, an exhaust rocker arm, an intake hydraulic tappet, an exhaust hydraulic tappet, an intake valve, an exhaust door, intake valve spring and exhaust valve spring, the intake rocker arm includes the intake rocker arm body and the intake rocker arm bearing rotatably supported in the middle of the intake rocker arm body, the exhaust rocker arm includes the exhaust rocker arm body and Rotate the exhaust rocker arm bearing supported in the middle of the exhaust rocker arm body, the intake rocker arm bearing is in rolling contact with the cam of the intake camshaft, the exhaust rocker arm bearing is in rolling contact with the cam of the exhaust camshaft, The outer end of the intake rocker arm body is connected to the upper end of the intake hydraulic tappet, the inner end of the intake rocker arm body is connected to the upper end of the intake valve, and the outer end of the exhaust rocker arm body is connected to the upper end of the exhaust hydraulic tappet. Connected, the inner end of the exhaust rocker arm body is connected with the upper end of the exhaust valve. The engine gas distribution mechanism of the utility model has the advantages of compact structure and reliable transmission.

Description

Engine valve train and engine

technical field

The utility model belongs to the technical field of engines, in particular to an engine gas distribution mechanism and an engine.

Background technique

Gasoline engine gas distribution mechanism mainly includes overhead single camshaft and overhead double camshaft, and the driving forms of valve mainly include direct drive and indirect drive with rocker arm.

The parts involved in the engine valve train are many and complex. The performance of an engine is 45%-50% determined by the performance and capability of the valve train. In order to cooperate with the use of some new technologies, such as variable valve timing system (VVT) and Variable valve lift system (VVL), newly designed gasoline engines basically adopt flexible double overhead camshafts. In order to improve driving efficiency and reduce friction, roller rocker arms with hydraulic tappets are often used to drive valves.

The Chinese patent with the authorized notification number CN202628209U discloses a gas distribution mechanism, which includes a cylinder head and a combustion chamber arranged at the lower part of the cylinder head. There is an intake valve, an exhaust valve is set at the connection between the exhaust passage and the combustion chamber, a valve spring is set on the intake valve and the exhaust valve respectively, and an intake rocker arm and an intake hydraulic lifter are installed above the intake valve. There is an exhaust rocker arm and an exhaust hydraulic tappet above the exhaust valve, the outer end of the intake rocker arm is connected to the upper end of the intake valve, and the inner end of the intake rocker arm is connected to the upper end of the intake hydraulic tappet , the outer end of the exhaust rocker arm is connected to the upper end of the exhaust valve, and the inner end of the exhaust rocker arm is connected to the upper end of the exhaust hydraulic tappet, so that the intake hydraulic tappet and the exhaust hydraulic tappet are respectively arranged in The inner side of the intake valve and the inner side of the exhaust valve need to be reserved between the intake valve and the exhaust valve for the assembly space of the intake hydraulic tappet and the exhaust hydraulic tappet, resulting in a gap between the intake valve and the exhaust valve. The included angle is usually large, the distance between the intake camshaft and the exhaust camshaft is relatively large, and the entire valve train is not compact enough.

Utility model content

The technical problem to be solved by the utility model is to provide an engine gas distribution mechanism for the defect that the existing engine gas distribution mechanism is not compact enough.

The technical solution adopted by the utility model to solve the problems of the technologies described above is as follows:

An engine valve mechanism is provided, including an intake camshaft, an exhaust camshaft, an intake rocker arm, an exhaust rocker arm, an intake hydraulic tappet, an exhaust hydraulic tappet, an intake valve, an exhaust valve, an intake valve spring and exhaust valve spring, the intake valve spring is sleeved on the intake valve, the exhaust valve spring is sleeved on the exhaust valve, the intake camshaft and the The exhaust camshaft constitutes a double overhead camshaft, the intake rocker arm includes an intake rocker arm body and an intake rocker arm bearing rotatably supported in the middle of the intake rocker arm body, and the exhaust rocker arm includes an exhaust The air rocker arm body and the exhaust rocker arm bearing rotatably supported in the middle of the exhaust rocker arm body, the intake camshaft and the exhaust camshaft are arranged on the intake rocker arm and the exhaust camshaft respectively. Above the rocker arm, the intake rocker arm bearing is in rolling contact with the cam of the intake camshaft, the exhaust rocker arm bearing is in rolling contact with the exhaust camshaft cam, and the intake rocker The outer end of the arm body is connected with the upper end of the intake hydraulic tappet, the inner end of the intake rocker arm body is connected with the upper end of the intake valve, and the outer end of the exhaust rocker arm body is connected with the The upper end of the exhaust hydraulic tappet is connected, and the inner end of the exhaust rocker arm body is connected with the upper end of the exhaust valve.

Further, the lower surface of the outer end of the intake rocker arm is formed with an intake rocker arm ball socket, and the upper end of the intake hydraulic tappet is formed with a first ball head accommodated in the intake rocker arm ball socket , the first ball head is limited in the intake rocker ball socket by a first stopper; the exhaust rocker ball socket is formed on the lower surface of the outer end of the exhaust rocker arm, and the row The upper end of the pneumatic tappet is formed with a second ball head accommodated in the ball socket of the exhaust rocker arm, and the second ball head is limited in the ball socket of the exhaust rocker arm by a second limiter .

Further, the distance between the axis of the intake camshaft and the bottom surface of the engine cylinder head is 133-136 mm, and the distance between the axis of the exhaust camshaft and the bottom surface of the engine cylinder head is 133-136 mm.

Further, the distance between the axis of the intake camshaft and the centerline of the cylinder bore is 57-59mm, and the distance between the axis of the exhaust camshaft and the centerline of the cylinder bore is 59-62mm.

Further, the distance between the center of the intake rocker ball socket and the centerline of the cylinder bore is 71-73mm, and the distance between the center of the exhaust rocker ball socket and the centerline of the cylinder bore is 72-74mm .

Further, the distance between the center of the intake rocker arm ball socket and the horizontal plane where the axes of the intake camshaft and exhaust camshaft are located is 35-37mm, and the center of the exhaust rocker arm ball socket and The distance between the axis of the intake camshaft and the horizontal plane where the axis of the exhaust camshaft is located is 35-37mm.

Further, the included angle between the axis of the intake valve and the central line of the cylinder bore is 14-16°, and the included angle between the axis of the exhaust valve and the central line of the cylinder bore is 13-15°.

Further, the cam of the intake camshaft is in contact with the intake rocker arm bearing on a first straight line, and the axis plane of the intake valve perpendicular to the axis of the intake camshaft is in contact with the first Lines intersect to form a first tangent point, and the angle between the perpendicular line from the first tangent point to the axis of the intake camshaft and the axis of the intake hydraulic tappet is 10-13°; The cam of the camshaft is in contact with the exhaust rocker arm bearing on a second straight line, and the axis plane of the exhaust valve perpendicular to the axis of the exhaust camshaft intersects with the second straight line to form a second tangent point, The included angle between the perpendicular line from the second tangent point to the axis of the exhaust camshaft and the axis of the exhaust hydraulic tappet is 10-13°

Further, the included angle between the axis of the intake hydraulic tappet and the axis of the intake valve is -3° to 3°, and the included angle between the axis of the exhaust hydraulic tappet and the axis of the exhaust valve The angle is -3°～3°. When the included angle between the axis of the intake hydraulic tappet and the axis of the intake valve is a negative value, it means that the axis of the intake hydraulic tappet rotates clockwise by the absolute value of the included angle to meet the intake valve. On the contrary, when the angle between the axis of the intake hydraulic tappet and the axis of the intake valve is positive, it means that the axis of the intake hydraulic tappet rotates counterclockwise by the angle with the The axis of the intake valve is parallel; similarly, when the angle between the axis of the exhaust hydraulic tappet and the axis of the exhaust valve is negative, it means that the axis of the exhaust hydraulic tappet rotates clockwise The absolute value of the angle is parallel to the axis of the exhaust valve; when the angle between the axis of the exhaust hydraulic tappet and the axis of the exhaust valve is positive, it means that the exhaust hydraulic tappet The axis of the exhaust valve is parallel to the axis of the exhaust valve after being rotated counterclockwise by the included angle.

Further, the intake rocker bearing and the exhaust rocker bearing are both roller bearings.

In the engine gas distribution mechanism of the utility model, the outer end of the intake rocker arm body is connected with the upper end of the intake hydraulic tappet, and the inner end of the intake rocker arm body is connected with the upper end of the intake valve. , the outer end of the exhaust rocker arm body is connected to the upper end of the exhaust hydraulic tappet, and the inner end of the intake rocker arm body is connected to the upper end of the exhaust valve, that is, the intake hydraulic tappet The pillar and the exhaust hydraulic tappet are respectively arranged on the outside of the intake valve and the exhaust valve, and most of the intake rocker arm body and the exhaust rocker arm body are respectively located on the intake valve valve and the outer side of the exhaust valve, so that there are no other valve train components between the intake valve and the exhaust valve, the intake valve and the exhaust valve can be closer, and the angle between the valves can be designed to be small enough. The distance between the intake camshaft and the exhaust camshaft can be small enough, so that the whole valve train can be more compact. In addition, the intake rocker arm and exhaust rocker arm are arranged on both sides of the intake valve and exhaust valve respectively, so that the position of the intake rocker arm and exhaust rocker arm can be better designed and arranged to meet the requirements of other conditions. The layout of the entire valve train. At the same time, the design margin of the cam profile is larger, which improves the safety of the moving parts of the valve train.

In addition, the utility model also provides an engine, which includes the above-mentioned engine gas distribution mechanism.

Description of drawings

Fig. 1 is a simplified drawing of an engine valve mechanism provided by an embodiment of the utility model;

Fig. 2 is a schematic structural view of an engine valve mechanism provided by an embodiment of the utility model;

Fig. 3 is an exploded view of parts of the engine valve mechanism provided by an embodiment of the present invention.

The reference signs in the accompanying drawings of the description are as follows:

1. Intake camshaft; 11. Cam of intake camshaft; 2. Exhaust camshaft; 21. Cam of exhaust camshaft; 3. Intake rocker arm; 31. Intake rocker arm body; 32. Inlet Air rocker arm bearing; 33. Intake rocker arm ball socket; 4. Exhaust rocker arm; 41. Exhaust rocker arm body; 42. Exhaust rocker arm bearing; 43. Exhaust rocker arm ball socket; 5. Intake air Hydraulic tappet; 51, first ball head; 6, exhaust hydraulic tappet; 61, second ball head; 7, intake valve; 8, exhaust valve; 91, intake valve spring; 92, exhaust valve Spring; 10, the first limiting part; 20, the second limiting part; 30, the bottom surface of the engine cylinder head.

Detailed ways

In order to make the technical problems, technical solutions and beneficial effects solved by the utility model clearer, the utility model will be further described in detail below in conjunction with the accompanying drawings and embodiments. It should be understood that the specific embodiments described here are only used to explain the utility model, and are not intended to limit the utility model.

As shown in Figures 1 to 3, the engine valve mechanism provided by an embodiment of the utility model includes an intake camshaft 1, an exhaust camshaft 2, an intake rocker arm 3, an exhaust rocker arm 4, an intake hydraulic pressure Tappet 5, exhaust hydraulic tappet 6, intake valve 7, exhaust valve 8, intake valve spring 91 and exhaust valve spring 92, the intake valve spring 91 is sleeved on the intake valve 7 , the exhaust valve spring 92 is sleeved on the exhaust valve 8, the intake camshaft 1 and the exhaust camshaft 2 form a double overhead camshaft, and the intake rocker arm 3 includes an intake The air rocker arm body 31 and the intake rocker arm bearing 32 rotatably supported in the middle of the intake rocker arm body 31 , the exhaust rocker arm 4 includes the exhaust rocker arm body 41 and the exhaust rocker arm body 41 rotatably supported on the exhaust rocker arm The exhaust rocker arm bearing 42 in the middle of the body 41, the intake camshaft 1 and the exhaust camshaft 2 are respectively arranged above the intake rocker arm 3 and the exhaust rocker arm 4, the intake camshaft The air rocker arm bearing 32 is in rolling contact with the cam 11 of the intake camshaft, and the exhaust rocker arm bearing 42 is in rolling contact with the cam 21 of the exhaust camshaft. The outer end is connected with the upper end of the intake hydraulic tappet 5, the inner end of the intake rocker arm body 31 is connected with the upper end of the intake valve 7, and the outer end of the exhaust rocker arm body 41 is connected with the exhaust rocker arm body 41. The upper end of the exhaust hydraulic tappet 6 is connected, and the inner end of the exhaust rocker arm body 41 is connected with the upper end of the exhaust valve 8 . Specifically, the inner end of the intake rocker arm body 31 is formed with an arc surface, and the upper end (rod end) of the intake valve 7 is in contact with the arc surface of the inner end of the intake rocker arm body 31; The inner end of the exhaust rocker arm body 41 is formed with an arc surface, and the upper end (rod end) of the exhaust valve 8 is in contact with the arc surface at the inner end of the exhaust rocker arm body 41 .

Usually, a combustion chamber is provided inside the cylinder head of the engine, and the combustion chamber communicates with the intake port and the exhaust port.

In this embodiment, the intake valve 7 is arranged at the connection between the intake passage and the combustion chamber, the exhaust valve 8 is arranged at the connection between the exhaust passage and the combustion chamber, and the connection between the intake passage and the combustion chamber is provided with a supporting intake valve spring. The platform of 91, the communication place of exhaust passage and combustion chamber is provided with the platform of supporting exhaust valve spring 92. The intake rocker arm 3 and the intake hydraulic tappet 5 are arranged above the intake valve 7 , while the exhaust rocker arm 4 and the exhaust hydraulic tappet 6 are arranged above the exhaust valve 8 .

In addition, holes for assembling the intake hydraulic tappets 5 and the exhaust hydraulic tappets 6 are also opened on the cylinder head of the engine.

In this embodiment, the intake rocker arm bearing 32 and the exhaust rocker arm bearing 42 are both roller bearings. In this way, both the intake rocker arm 3 and the exhaust rocker arm 4 are roller rocker arms.

In this embodiment, an intake rocker ball socket 33 is formed on the lower surface of the outer end of the intake rocker arm 3 , and an intake rocker ball socket 33 is formed on the upper end of the intake hydraulic tappet 5 . The first ball head 51 in the center and matched with the intake rocker arm ball socket 33, the first ball head 51 is limited in the intake rocker arm ball socket 33 by a first stopper 10; An exhaust rocker ball socket 43 is formed on the lower surface of the outer end of the exhaust rocker arm, and an exhaust rocker ball socket 43 is formed on the upper end of the exhaust hydraulic tappet 6, which is accommodated in the exhaust rocker ball socket 43 and is connected with the exhaust rocker arm. The rocker arm ball socket 43 fits with the second ball head 61 , and the second ball head 61 is limited in the exhaust rocker arm ball socket 43 by a second limiting member 20 . The contact between the intake hydraulic tappet 5 and the intake rocker arm 3 , and the contact between the exhaust hydraulic tappet 6 and the exhaust rocker arm 4 are realized through the above method.

In this embodiment, as shown in Figure 1, the specific arrangement of the valve mechanism is as follows:

The distance between the axis of the intake camshaft 1 and the bottom surface 30 of the engine cylinder head is 133-136 mm, and the distance between the axis of the exhaust camshaft 2 and the bottom surface 30 of the engine cylinder head is 133-136 mm.

The distance between the axis of the intake camshaft 1 and the centerline Z1 of the cylinder bore (that is, the distance between the cam center O3 of the intake camshaft and the centerline Z1 of the cylinder bore) is 57-59 mm, and the exhaust camshaft 2 The distance between the axis of and the centerline Z1 of the cylinder bore (that is, the distance from the cam center O4 of the exhaust camshaft to the centerline Z1 of the cylinder bore) is 59-62mm.

The distance between the center O1 of the intake rocker arm ball socket 33 and the center line Z1 of the cylinder bore is 71-73 mm, and the distance between the center O2 of the exhaust rocker arm ball socket 43 and the center line Z1 of the cylinder bore is 72 ~ 74mm.

The distance between the center O1 of the intake rocker arm ball socket 33 and the horizontal plane S1 where the axes of the intake camshaft and exhaust camshaft are located is 35-37mm, and the center of the exhaust rocker arm ball socket 43 The distance between O2 and the horizontal plane S1 where the axis of the intake camshaft and the axis of the exhaust camshaft are located is 35-37mm.

The included angle between the axis Z2 of the intake valve 7 and the central line Z1 of the cylinder bore is 14-16°, and the included angle between the axis Z3 of the exhaust valve 8 and the central line Z1 of the cylinder bore is 13-15°. °.

The cam 11 of the intake camshaft and the intake rocker arm bearing 32 are in contact with the first straight line, and the axis plane of the intake valve 7 perpendicular to the axis of the intake camshaft 1 is in contact with the first A straight line intersects to form the first tangent point Q1, and the angle between the perpendicular line from the first tangent point Q1 to the axis of the intake camshaft and the axis Z4 of the intake hydraulic tappet 5 is 10-13° The cam 21 of the exhaust camshaft and the exhaust rocker arm bearing 42 are in contact with the second straight line, and the axis plane of the exhaust valve 8 perpendicular to the axis of the exhaust camshaft 2 is in contact with the exhaust valve 8 The second straight line intersects to form a second tangent point Q2, and the angle between the perpendicular line from the second tangent point Q2 to the axis of the exhaust camshaft and the axis Z5 of the exhaust hydraulic tappet 6 is 10-13° .

The included angle between the axis Z4 of the intake hydraulic tappet 5 and the axis Z2 of the intake valve 7 is -3° to 3°, and the axis Z5 of the exhaust hydraulic tappet 6 and the axis Z2 of the exhaust valve 8 The included angle of the axis Z3 is -3°～3°. When the angle between the axis Z4 of the intake hydraulic tappet 5 and the axis Z2 of the intake valve 7 is a negative value, it means that the axis Z4 of the intake hydraulic tappet 5 rotates clockwise. and then parallel to the axis Z2 of the intake valve 7; on the contrary, when the angle between the axis Z5 of the exhaust hydraulic tappet 6 and the axis Z3 of the exhaust valve 8 is a positive value, it means that the intake hydraulic pressure The axis Z4 of the tappet 5 is parallel to the axis Z2 of the intake valve 7 after rotating the included angle counterclockwise; similarly, the axis Z5 of the exhaust hydraulic tappet 6 is parallel to the axis Z3 of the exhaust valve 8 When the included angle is a negative value, it means that the axis Z5 of the exhaust hydraulic tappet 6 is parallel to the axis Z3 of the exhaust valve 8 after the axis Z5 of the exhaust hydraulic tappet 6 rotates clockwise by the absolute value; When the included angle between the axis Z5 and the axis Z3 of the exhaust valve 8 is a positive value, it means that the axis Z5 of the exhaust hydraulic tappet 6 rotates counterclockwise by the included angle and is parallel to the axis Z3 of the exhaust valve 8 .

It should be understood that Figure 1 only shows the relative positional relationship (design parameters) of the various components of the valve train, please refer to Figure 2 and Figure 3 for specific structures.

Compared with the gas distribution mechanism of the existing layout, the valve mechanism with the above-mentioned arrangement form of this embodiment has improved the dynamics and motion passability of the valve mechanism by nearly 20% in the actual process of cam profile design. The design margin of the cam profile is improved, the design of the cam profile is easier, the processing of the camshaft is easier and the processing cost is lower.

In addition, an embodiment of the present invention also provides an engine, which includes the above-mentioned engine valve mechanism.

The above descriptions are only preferred embodiments of the present utility model, and are not intended to limit the present utility model. Any modifications, equivalent replacements and improvements made within the spirit and principles of the present utility model shall be included in this utility model. within the scope of protection of utility models.

Claims (10)

1. A valve mechanism for an engine, characterized in that it comprises an intake camshaft, an exhaust camshaft, an intake rocker arm, an exhaust rocker arm, an intake hydraulic tappet, an exhaust hydraulic tappet, an intake valve, Exhaust valve, intake valve spring and exhaust valve spring, the intake valve spring is sleeved on the intake valve, the exhaust valve spring is sleeved on the exhaust valve, the intake valve The camshaft and the exhaust camshaft form a double overhead camshaft. The intake rocker arm includes an intake rocker arm body and an intake rocker arm bearing rotatably supported in the middle of the intake rocker arm body. The air rocker arm includes an exhaust rocker arm body and an exhaust rocker arm bearing rotatably supported in the middle of the exhaust rocker arm body. The intake camshaft and the exhaust camshaft are respectively arranged on the intake rocker arm and above the exhaust rocker arm, the intake rocker arm bearing is in rolling contact with the cam of the intake camshaft, the exhaust rocker arm bearing is in rolling contact with the exhaust camshaft cam, The outer end of the intake rocker arm body is connected to the upper end of the intake hydraulic tappet, the inner end of the intake rocker arm body is connected to the upper end of the intake valve, and the exhaust rocker arm body is The outer end is connected with the upper end of the exhaust hydraulic tappet, and the inner end of the exhaust rocker arm body is connected with the upper end of the exhaust valve. 2. The engine valve mechanism according to claim 1, characterized in that, the lower surface of the outer end of the intake rocker arm is formed with an intake rocker ball socket, and the upper end of the intake hydraulic tappet is formed with a The first ball head in the ball socket of the intake rocker arm, the first ball head is limited in the ball socket of the air intake rocker arm by a first limiter; the outer surface of the exhaust rocker arm The lower surface of the end is formed with an exhaust rocker ball socket, and the upper end of the exhaust hydraulic tappet is formed with a second ball head accommodated in the exhaust rocker ball socket, and the second ball head passes through a second The limiting member is limited in the ball socket of the exhaust rocker arm. 3. The engine valve train according to claim 1 or 2, characterized in that the distance between the axis of the intake camshaft and the bottom surface of the engine cylinder head is 133-136 mm, and the axis of the exhaust camshaft and the bottom surface of the engine cylinder The distance between the bottom surface of the engine cylinder head is 133-136mm. 4. The engine valve train according to claim 1 or 2, characterized in that the distance between the axis of the intake camshaft and the centerline of the cylinder bore is 57-59mm, and the axis of the exhaust camshaft and the centerline of the cylinder bore The distance between the centerlines of the cylinder bores is 59-62 mm. 5. The engine valve mechanism according to claim 2, characterized in that the distance between the center of the intake rocker arm ball socket and the centerline of the cylinder bore is 71-73 mm, and the exhaust rocker arm ball socket The distance between the center and the centerline of the cylinder bore is 72-74mm. 6. The engine valve train according to claim 2, wherein the distance between the center of the intake rocker arm socket and the horizontal plane where the axis of the intake camshaft and the axis of the exhaust camshaft are located is 35-37mm, the distance between the center of the exhaust rocker arm ball socket and the horizontal plane where the axis of the intake camshaft and the axis of the exhaust camshaft are located is 35-37mm. 7. The engine valve train according to claim 1 or 2, characterized in that the angle between the axis of the intake valve and the centerline of the cylinder bore is 14-16°, and the axis of the exhaust valve and the center line of the cylinder hole The included angle between the centerlines of the cylinder bores is 13-15°. 8. The engine gas distribution mechanism according to claim 1 or 2, characterized in that the cam of the intake camshaft and the intake rocker arm bearing are in contact with a first straight line, and the vertical direction of the intake valve The axis plane of the axis of the intake camshaft intersects the first straight line to form a first tangent point, and the perpendicular line from the first tangent point to the axis of the intake camshaft and the intake hydraulic pressure The angle between the axes of the tappets is 10-13°; the cam of the exhaust camshaft and the exhaust rocker arm bearing are in contact with the second straight line, and the exhaust valve is perpendicular to the exhaust camshaft The axis plane of the axis intersects the second straight line to form a second tangent point, and the angle between the perpendicular line from the second tangent point to the axis of the exhaust camshaft and the axis of the exhaust hydraulic tappet is 10 ~13°. 9. The engine valve train according to claim 1 or 2, characterized in that the included angle between the axis of the intake hydraulic tappet and the axis of the intake valve is -3° to 3°, and the The included angle between the axis of the exhaust hydraulic tappet and the axis of the exhaust valve is -3° to 3°. 10. An engine, characterized in that the engine comprises the engine valve train according to any one of claims 1-9.