阅读说明：本技术 一种进气门、气缸盖及燃气发动机 (Intake valve, cylinder cover and gas engine ) 是由 李卫 吕顺 王霞 于 2021-08-19 设计创作，主要内容包括：本发明公开了一种进气门、气缸盖及燃气发动机,包括进气门杆和进气门盘,进气门盘的底面边沿的局部向下凸起形成阻流凸起部,且当进气门安装至气缸盖的进气喉口时,阻流凸起部位于靠近该进气喉口所对应的排气喉口的一侧,进气门杆的外周设有用于与气门导管滑动配合并限制进气门与气门导管相对转动的限位部。本发明通过在进气门盘的底面设置阻流凸起部,在进气过程中能够使更多进气气流向排气喉口方向运动,同时能够避免进气气流在进气门盘边缘处产生的局部卷流作用,从而有利于气流在气缸内形成大尺度的滚流运动,同时,在压缩中后期,能够利用阻流凸起部形成更多的湍流运动,提高火花塞附近的湍动能,加快火焰传播速度,提升燃气发动机的热效率。(The invention discloses an intake valve, a cylinder cover and a gas engine, which comprise an intake valve rod and an intake valve disk, wherein the local part of the bottom edge of the intake valve disk protrudes downwards to form a flow-resisting protruding part, when the intake valve is installed on an intake throat of the cylinder cover, the flow-resisting protruding part is positioned at one side close to an exhaust throat corresponding to the intake throat, and the periphery of the intake valve rod is provided with a limiting part which is used for being matched with a valve guide pipe in a sliding way and limiting the relative rotation of the intake valve and the valve guide pipe. The bottom surface of the air inlet valve disc is provided with the flow choking bulge part, so that more air inflow can move towards the direction of the exhaust throat in the air inlet process, and the local swirling action of the air inflow at the edge of the air inlet valve disc can be avoided, so that the air flow can form large-scale tumble motion in the air cylinder, and meanwhile, in the middle and later stages of compression, more turbulent motion can be formed by using the flow choking bulge part, the turbulent motion energy near a spark plug is improved, the flame propagation speed is accelerated, and the heat efficiency of a gas engine is improved.)

1. The utility model provides an inlet valve, the inlet valve includes inlet valve pole (1) and inlet valve dish (2), its characterized in that, the local downwardly protruding formation choked flow bellying (3) of bottom surface border of inlet valve dish (2), and when the inlet valve is installed to the intake throat of cylinder head, choked flow bellying (3) are located and are close to this intake throat (4) one side of the exhaust throat that corresponds, the periphery of inlet valve pole (1) is equipped with and is used for with valve guide sliding fit and restriction the inlet valve with the spacing portion of valve guide relative rotation.

2. An intake valve according to claim 1, wherein the projection of the flow blocking protrusion (3) on the bottom surface of the intake valve disk (2) is an arcuate projection, and the convex side of the arcuate projection faces outward in the radial direction of the intake valve disk (2), and the width of the middle of the arcuate projection is greater than the width of the two ends thereof.

3. An inlet valve according to claim 2, characterised in that the arcuate projection is at least partly located inside the bottom end face of the inlet valve disc (2); or the arc projection is at least partially positioned outside the bottom end surface of the air inlet valve disc (2).

4. An intake valve according to claim 2, wherein the height H at which the flow-obstructing projection (3) is downwardly convex with respect to the bottom surface of the intake valve disc (2) satisfies the relationship: h is more than 0 and less than or equal to 0.2D, wherein D is the diameter of the bottom end face of the air inlet valve disc of the air inlet valve.

5. An inlet valve according to claim 2, characterised in that the arcuate projection is arranged along a circumferential edge of the inlet valve disc (2) and covers an angle θ in the circumferential direction of the inlet valve disc (2) which satisfies the relation: theta is more than 0 and less than or equal to 240 degrees.

6. An intake valve according to claim 2, wherein the joining position of the surface of the flow blocking protrusion (3) facing the center of the intake valve disc (2) and the bottom end surface of the intake valve disc (2) is a smooth curved surface.

7. The intake valve according to claim 6, wherein the smooth curved surface is an inward concave arc-shaped surface formed by rounding off the joining position, and a rounding radius R of the inward concave arc-shaped surface satisfies a relationship: r is more than 0 and less than or equal to 0.2D, wherein D is the diameter of the bottom end face of the air inlet valve disc of the air inlet valve.

8. An inlet valve according to any of claims 1-7, characterized in that the limiting part is a limiting projection or a limiting groove provided at the periphery of the inlet valve stem (1).

9. A cylinder cover is applied to a gas engine reformed on the basis of a diesel engine and comprises an air inlet throat (4) and an air outlet throat, wherein an air inlet valve seat ring (6) and an air inlet valve used for being matched with the air inlet valve seat ring (6) to open and close to realize the on-off control of air inlet are arranged in the air inlet throat (4), and the air inlet valve is the air inlet valve as claimed in any one of claims 1 to 8.

10. A cylinder head according to claim 9, characterized in that the intake throat (4) comprises a first intake throat (41) and a second intake throat (42), the intake valves being mounted in both the first intake throat (41) and the second intake throat (42), the exhaust throat comprising a first exhaust throat (51) arranged opposite the first intake throat (41) and a second exhaust throat (52) arranged opposite the second intake throat (42).

11. The cylinder head according to claim 10, wherein an angle θ between a line connecting the center of the intake valve corresponding to the first intake throat (41) and the center of the flow-blocking boss (3) on the intake valve plate of the intake valve corresponding thereto and the axis (7) of the crankshaft is set to₁The included angle between the connecting line of the center of the intake valve corresponding to the first intake throat (41) and the center of the exhaust valve corresponding to the first exhaust throat (51) and the axis (7) of the crankshaft is theta₂Wherein theta₁And theta₂Satisfies the relationship: theta is not less than 0₁≤2θ₂。

12. The cylinder head according to claim 10, wherein an angle θ between a line connecting the center of the intake valve corresponding to the second intake throat (42) and the center of the flow-blocking projection (3) on the intake valve plate of the intake valve corresponding thereto and the axis (7) of the crankshaft is set to₃The included angle between the connecting line of the center of the intake valve corresponding to the second intake throat (42) and the center of the exhaust valve corresponding to the second exhaust throat (52) and the axis (7) of the crankshaft is theta₄Wherein theta₃And theta₄Satisfies the relationship: theta is not less than 0₃≤2θ₄。

13. The cylinder head according to claim 10, characterized in that the intake valve retainer (6) includes a first intake valve retainer (61) disposed in the first intake throat (41) and a second intake valve retainer (62) disposed in the second intake throat (42), and the first intake valve retainer (61) has a height H from the bottom surface of the cylinder head₁Is greater than the height H of the second intake valve seat ring (62) from the bottom surface of the cylinder head₂。

14. The cylinder head of claim 13, wherein the first intake valve seat insert (61) has a height H from the bottom surface of the cylinder head₁A height H from the second intake valve seat ring (62) to the bottom surface of the cylinder head₂Height difference H of₃Satisfies the relationship: h is more than 0₃And D is not more than 0.2D, wherein D is the diameter of the bottom end face of the inlet valve disc of the inlet valve.

15. The cylinder head of claim 13, wherein H is₃The following relations are satisfied: h is more than 0₃≤6mm。

16. The cylinder head according to claim 13, characterized in that the first inlet throat (41) is located at a smaller distance from the head inlet than the second inlet throat (42), a first inlet chamfer (81) being formed below the first inlet throat (41) in correspondence with the first inlet seat (61), and a second inlet chamfer (82) being formed below the second inlet throat (42) in correspondence with the second inlet seat (62).

17. The cylinder head according to claim 16, characterized in that the center of the first intake chamfer (81) is offset in the direction of the first exhaust throat (51) by a first preset distance with respect to the center of the first intake throat (41); the center of the second air inlet chamfer (82) is offset by a second preset distance towards the second exhaust throat (52) relative to the center of the second air inlet throat (42).

18. The cylinder head of claim 17, wherein said first predetermined distance is equal to or different from said second predetermined distance.

19. The cylinder head according to claim 17, characterized in that the first inlet chamfer (81) and the second inlet chamfer (82) have the same or different structural shape.

20. The cylinder head according to claim 9, characterized in that a tumble flow cusp (9) is provided in the intake valve seat insert (6) on the side away from the exhaust throat, and the axial projection of the tumble flow cusp (9) on the upper end face of the intake valve seat insert (6) is a cusp projection forming a convex area that projects from the inner edge of the intake valve seat insert (6) in the radial direction towards the center of the intake valve seat insert (6), and the width of the middle of the cusp projection is greater than the width of the two ends thereof.

21. A cylinder head according to claim 20, characterized in that the pointed projection is a crescent-shaped area with the concave side arranged towards the centre of the inlet valve seat insert (6).

22. A gas engine comprising a cylinder head, characterized in that the cylinder head is a cylinder head according to any one of claims 9-21.

Technical Field

The invention relates to the technical field of air inlet of engines, in particular to an inlet valve, a cylinder cover and a gas engine.

Background

With the development of gas engine technology, more and more gas engines are transformed on the basis of diesel engines at present. In the case of a diesel engine, the combustion mode is diffusion combustion, and a certain degree of swirl helps the oil bundles to mix with air, thereby improving the combustion process, so that an air inlet passage in the cylinder head of the engine is required to organize the air flow to generate a sufficient swirl ratio during the intake process. Wherein, the vortex refers to the gas rotational flow movement organized around the cylinder axial direction.

However, the combustion mode of the gas engine is premixed combustion, the requirement on the strength of vortex is not high, and small-scale turbulent motion is needed to form a flame wrinkle surface, so that the flame propagation speed is increased, and the heat efficiency is improved, wherein the turbulent motion refers to small rotational flow which is generated in a flow field when the air flow speed is high and has unfixed directions, and is different from laminar motion. For a gas engine, the strength of the vortex does not need to be increased, and the increase of the tumble strength in the cylinder can be beneficial to forming turbulence at the end of compression and generating enough turbulent kinetic energy when the piston moves up to the top dead center, so that the aim of optimizing combustion is fulfilled. Wherein, the tumble refers to the gas rotational flow motion of which the rotation central axis is vertical to the axial direction of the cylinder sleeve.

Therefore, for the existing gas engine cylinder cover which is designed by integrally modifying the diesel engine cylinder cover, tumble flow required by the gas engine is difficult to generate in the cylinder.

In summary, how to improve tumble effect in a combustion chamber of a developed gas engine on the basis of improving a diesel engine has become a technical problem to be solved by those skilled in the art.

Disclosure of Invention

The invention aims to provide an inlet valve, a cylinder cover and a gas engine, which are used for improving the tumble effect in a combustion chamber of a developed gas engine on the basis of improving a diesel engine.

In order to achieve the purpose, the intake valve comprises an intake valve rod and an intake valve disk, wherein a local part of the bottom surface edge of the intake valve disk protrudes downwards to form a flow blocking protruding part, when the intake valve is installed on an intake throat of a cylinder cover, the flow blocking protruding part is positioned at one side close to an exhaust throat corresponding to the intake throat, and a limiting part which is used for being in sliding fit with a valve guide pipe and limiting the relative rotation of the intake valve and the valve guide pipe is arranged on the periphery of the intake valve rod.

Preferably, the projection of the flow blocking convex part on the bottom surface of the intake valve disc is an arc projection, the convex side of the arc projection faces outwards along the radial direction of the intake valve disc, and the width of the middle part of the arc projection is greater than the width of the two ends of the arc projection.

Preferably, the arcuate projection is at least partially located inside a bottom end face of the intake valve disk; or the arc projection is at least partially positioned outside the bottom end surface of the intake valve disc.

Preferably, the height H of the flow blocking protrusion protruding downward relative to the bottom surface of the intake valve disc satisfies the relationship: h is more than 0 and less than or equal to 0.2D, wherein D is the diameter of the bottom end face of the air inlet valve disc of the air inlet valve.

Preferably, the arc projection is arranged along the circumferential edge of the intake valve disc, and the arc projection covers an angle θ in the circumferential direction of the intake valve disc, which satisfies the relationship: theta is more than 0 and less than or equal to 240 degrees.

Preferably, the joint position of one surface of the flow blocking convex part facing the center of the intake valve disc and the bottom end surface of the intake valve disc is a smooth curved surface.

Preferably, the smooth curved surface is an inner concave arc-shaped surface formed by rounding at the joining position, and the radius R of the rounding of the inner concave arc-shaped surface satisfies the relationship: r is more than 0 and less than or equal to 0.2D, wherein D is the diameter of the bottom end face of the air inlet valve disc of the air inlet valve.

Preferably, the limiting part is a limiting protrusion or a limiting groove arranged on the periphery of the intake valve rod.

Compared with the introduction content of the background technology, the intake valve comprises an intake valve rod and an intake valve disc, wherein the local part of the bottom surface edge of the intake valve disc protrudes downwards to form a flow blocking protruding part, when the intake valve is installed on an intake throat of a cylinder cover, the flow blocking protruding part is positioned at one side close to an exhaust throat corresponding to the intake throat, and a limiting part used for being in sliding fit with a valve guide pipe and limiting the relative rotation of the intake valve and the valve guide pipe is arranged on the periphery of the intake valve rod. This (air) intake valve is after installing the cylinder head to the engine, when the valve is opened, the air current gets into the cylinder through the throat of admitting air, because the choked flow bellying is located in the one side of being close to the exhaust throat that this throat of admitting air corresponds, and simultaneously, spacing portion can avoid relative rotation between (air) intake valve and the valve guide, thereby guarantee that the choked flow bellying all the time arranges towards exhaust throat one side, consequently, when the air current flows in the cylinder, the choked flow bellying can block partial air flow and move to throat one side of admitting air, make more air flows to exhaust throat direction motion, the air current forms the large-scale tumble motion more easily in the cylinder, also can promote the tumble effect in the combustion chamber of the gas engine of development on the basis of diesel engine. Meanwhile, when the inlet airflow flows through the edge of the inlet valve disc on one side of the exhaust throat, the flow blocking bulge part can also reduce the local swirling action of the inlet airflow generated at the side edge, namely, the flow blocking bulge part can enable most of the inlet airflow to flow towards the direction of the exhaust throat, so that the inlet airflow is prevented from generating violent small-scale winding motion towards the center of the inlet valve disc at the side edge, the energy loss of the inlet airflow is favorably reduced, and the large-scale tumble motion can be continuously formed in the cylinder. In addition, in the middle and later stages of compression, after the large-scale tumble motion is continuously compressed, the airflow which rapidly flows below the air inlet valve disc can be severely disturbed by the flow blocking bulge part, so that more turbulent motion is formed, the turbulent motion energy near the spark plug is improved, the flame propagation speed near the air inlet valve and near the exhaust valve is accelerated, and the heat efficiency of the gas engine can be improved.

In addition, the invention also provides a cylinder cover, which is applied to a gas engine reformed on the basis of a diesel engine and comprises an air inlet throat and an air outlet throat, wherein an air inlet valve seat ring and an air inlet valve used for realizing the on-off control of air inlet by matching with the air inlet valve seat ring are arranged in the air inlet throat, and the air inlet valve is the air inlet valve described in any scheme. Since the intake valve has the technical effects, the cylinder head provided with the intake valve also has the corresponding technical effects, and the description is omitted.

Preferably, the intake throat includes a first intake throat and a second intake throat, the intake valves are installed in the first intake throat and the second intake throat, and the exhaust throat includes a first exhaust throat arranged opposite to the first intake throat and a second exhaust throat arranged opposite to the second intake throat.

Preferably, an included angle between a connecting line of the center of the intake valve corresponding to the first intake throat and the center of the flow blocking convex part on the intake valve disc of the intake valve corresponding to the first intake throat and the axis of the crankshaft is theta₁The included angle between the connecting line of the center of the intake valve corresponding to the first intake throat and the center of the exhaust valve corresponding to the first exhaust throat and the axis of the crankshaft is theta₂Wherein theta₁And theta₂Satisfies the relationship: theta is not less than 0₁≤2θ₂。

Preferably, an included angle between a connecting line of the center of the intake valve corresponding to the second intake throat and the center of the flow blocking convex part on the intake valve disc of the intake valve corresponding to the second intake throat and the axis of the crankshaft is theta₃The included angle between the connecting line of the center of the intake valve corresponding to the second intake throat and the center of the exhaust valve corresponding to the second exhaust throat and the axis of the crankshaft is theta₄Wherein theta₃And theta₄Satisfies the relationship: theta is not less than 0₃≤2θ₄。

Preferably, the intake valve seat ring comprises a first intake valve seat ring arranged in the first air inlet throat and a second intake valve seat ring arranged in the second air inlet throat, and the height H of the first intake valve seat ring from the bottom surface of the cylinder cover₁The distance between the second air inlet valve and the seat ring of the air cylinder is larger than that between the second air inlet valve and the seat ring of the air cylinderHeight H of the cover bottom surface₂。

Preferably, the height H of the first intake valve seat from the bottom surface of the cylinder head₁The height H from the second air inlet valve seat ring to the bottom surface of the cylinder cover₂Height difference H of₃Satisfies the relationship: h is more than 0₃And D is not more than 0.2D, wherein D is the diameter of the bottom end face of the inlet valve disc of the inlet valve.

Preferably, H₃The following relations are satisfied: h is more than 0₃≤6mm。

Preferably, the distance between the first air inlet throat and the cylinder cover air inlet is smaller than the distance between the second air inlet throat and the cylinder cover air inlet, a first air inlet chamfer is formed below the first air inlet throat corresponding to the first air inlet seat ring, and a second air inlet chamfer is formed below the second air inlet throat corresponding to the second air inlet seat ring.

Preferably, the center of the first air inlet chamfer is offset by a first preset distance relative to the center of the first air inlet throat in the direction of the first exhaust throat; and the center of the second air inlet chamfer is offset by a second preset distance towards the direction of the second exhaust throat relative to the center of the second air inlet throat.

Preferably, the first preset distance and the second preset distance are equal or different.

Preferably, the first air inlet chamfer and the second air inlet chamfer have the same or different structural shapes.

Preferably, a tumble sharp angle is arranged on one side, far away from the exhaust throat, in the intake valve seat ring, the axial projection of the tumble sharp angle on the upper end surface of the intake valve seat ring is a sharp angle projection, the sharp angle projection forms a convex area which protrudes from the edge on the inner side of the intake valve seat ring to the center of the intake valve seat ring along the radial direction, and the width of the projection of the sharp angle on the middle part of the intake valve seat ring along the circumferential direction is greater than the width of the two ends of the intake valve seat ring.

Preferably, the sharp corner projects as a crescent shaped region with the concave side disposed towards the centre of the inlet valve seat insert.

In addition, the invention also provides a gas engine, which comprises a cylinder cover, wherein the cylinder cover is the cylinder cover described in any scheme, and the cylinder cover has the technical effects, so that the gas engine with the cylinder cover also has the corresponding technical effects, and the details are not repeated.

Drawings

FIG. 1 is a schematic structural view of an intake valve provided in an embodiment of the invention;

FIG. 2 is a schematic structural diagram of a bottom view of an intake valve disk provided in an embodiment of the present invention;

FIG. 3 is a schematic structural diagram of a feature that a flow blocking protrusion is arranged on the bottom edge of an intake valve disc in the embodiment of the present invention;

FIG. 4 is a schematic view of simulation of airflow movement in a combustion chamber without a flow blocking protrusion on an intake valve disc of a conventional intake valve;

FIG. 5 is a schematic view of simulation of airflow movement in a combustion chamber with a flow blocking protrusion arranged at the bottom of an intake valve disc according to an embodiment of the present invention;

FIG. 6 is a schematic view of an arrangement of flow blocking bosses of intake valves installed at two intake throats provided in an embodiment of the present invention;

FIG. 7 is a schematic view of a high-low arrangement of two intake valve seats on a cylinder head according to an embodiment of the present invention;

FIG. 8 is a schematic structural diagram of a tumble flow tip angle disposed on an intake valve seat ring according to an embodiment of the present invention;

fig. 9 is a schematic structural view of two intake valve seat rings provided with tumble flow sharp corners in the embodiment of the present invention;

fig. 10 is a graph comparing the tumble ratio of the present invention solution with the prior art solution.

In the context of figures 1-9 of the drawings,

the device comprises an intake valve rod 1, an intake valve disc 2, a flow blocking bulge part 3, an intake throat 4, a first intake throat 41, a second intake throat 42, a first exhaust throat 51, a second exhaust throat 52, an intake valve seat ring 6, a first intake valve seat ring 61, a second intake valve seat ring 62, the axis 7 of a crankshaft, a first intake chamfer 81, a second intake chamfer 82, a tumble sharp angle 9, an intake passage 10, a first intake passage 11, a second intake passage 12 and a cylinder cover intake port 13.

Detailed Description

The core of the invention is to provide an inlet valve, a cylinder cover and a gas engine, so as to improve the tumble effect in a combustion chamber of the developed gas engine on the basis of improving a diesel engine.

In order to make those skilled in the art better understand the technical solutions provided by the present invention, the technical solutions in the embodiments of the present application will be clearly and completely described below with reference to the drawings in the embodiments of the present application, and it is obvious that the described embodiments are only a part of the embodiments of the present application, and not all embodiments. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present application.

As shown in fig. 1-3, an intake valve according to an embodiment of the present invention includes an intake valve stem 1 and an intake valve disk 2, where a part of a bottom edge of the intake valve disk 2 protrudes downward to form a flow-blocking protrusion 3, and when the intake valve is mounted to an intake throat of a cylinder head, the flow-blocking protrusion 3 is located at a side close to an exhaust throat corresponding to the intake throat 4, and a limiting portion for slidably engaging with a valve guide and limiting relative rotation of the intake valve and the valve guide is provided at an outer periphery of the intake valve stem 1.

This (air) intake valve is after installing the cylinder head to the engine, when the engine cylinder breathes in, the valve is opened, the air current gets into the cylinder through the throat that admits air, because choked flow bellying is located the one side of being close to the exhaust throat that this throat that admits air corresponds, and simultaneously, relative rotation between (air) intake valve and the valve guide can be avoided to spacing portion, thereby guarantee that choked flow bellying all the time arranges towards exhaust throat one side, consequently, when the air current flows in the cylinder, choked flow bellying can block partial air current to the motion of throat that admits air one side, make more air currents to exhaust throat direction motion, the air current forms large-scale tumble motion more easily in the cylinder, also can promote the tumble effect in the gas engine's that improves the development on diesel engine's the basis. Meanwhile, when the intake airflow flows through the edge of the intake valve disc 2 towards one side of the exhaust throat, the flow blocking protrusion 3 can also reduce the local swirling action of the intake airflow generated at the side edge, namely, the flow blocking protrusion 3 can enable most of the intake airflow to flow towards the direction of the exhaust throat, so that the intake airflow is prevented from generating violent small-scale winding movement towards the center of the intake valve disc 2 at the side edge, the energy loss of the intake airflow is reduced, and the large-scale tumble motion can be formed in the cylinder continuously. In addition, in the middle and later stages of compression, after the large-scale tumble motion is continuously compressed, the airflow which rapidly flows below the air inlet valve disc 2 can be severely disturbed by the flow blocking convex parts 3, so that more turbulent motion is formed, the turbulent kinetic energy near the spark plug is improved, the flame propagation speed near the air inlet valve and near the exhaust valve is accelerated, and the heat efficiency of the gas engine can be improved.

Referring to fig. 10, compared with the prior art (i.e. the prior art does not design the flow blocking protrusion below the intake valve disc), when the valve lift is small, the intake airflow mainly enters the cylinder by the negative pressure in the cylinder, and because the flow blocking protrusion 3 is used in the present embodiment to avoid the local entrainment effect of the intake airflow generated at the edge of the intake valve disc 2 facing one side of the exhaust throat, the present invention can maintain high intake energy, so that the tumble motion can be more stable and the intensity is higher.

In order to better understand the technical effect achieved by the technical scheme of the invention, as shown in fig. 4, the air flow motion in the combustion chamber of the traditional intake valve disk without the flow-resisting convex part is simulated, as shown in fig. 5, the air flow motion in the combustion chamber of the intake valve disk with the flow-resisting convex part at the bottom is simulated, and through simulation calculation, it can be observed that after the arrangement of the flow-resisting convex part at the bottom of the intake valve disk is adopted, the air flow in the cylinder has obvious large-scale tumble effect.

In some specific embodiments, the projection of the flow blocking protrusion 3 on the bottom surface of the intake valve disk 2 may be specifically an arcuate projection, and the convex side of the arcuate projection faces outwards in the radial direction of the intake valve disk 2, and the width of the middle of the arcuate projection is greater than the width of the two ends of the arcuate projection, for example, the projection may be designed as a crescent projection structure, but is not limited to a crescent structure.

Note that the arcuate projection is at least partially located inside the bottom end face of the intake valve disk 2; or the arc projection is at least partially positioned at the outer side of the bottom end surface of the air inlet valve disc 2, and the arrangement can be selected according to actual requirements in the practical application process.

In some more specific embodiments, in order to adapt to engines of different models, the height H of the flow-blocking projection 3 protruding downward relative to the bottom surface of the intake valve disc 2 may be specifically selected to satisfy the relationship: h is more than 0 and less than or equal to 0.05D; or H is more than 0 and less than or equal to 0.1D; or H is more than 0 and less than or equal to 0.2D. And D is the diameter of the bottom end surface of the inlet valve disc of the inlet valve. In the practical application process, corresponding design parameters can be selected according to specific models.

In a further embodiment, the arcuate projection may be specifically arranged along a circumferential edge of the intake valve disc 2, and in order to accommodate different models of engines, the arcuate projection covers an angle θ in the circumferential direction of the intake valve disc 2, specifically selected to satisfy the relationship: theta is more than 0 and less than or equal to 60 degrees; or theta is more than 0 and less than or equal to 120 degrees; or theta is more than 0 and less than or equal to 240 degrees. In the practical application process, corresponding design parameters can be selected according to specific models and design requirements.

In some specific embodiments, the joint position of the side of the choke boss 3 facing the center of the intake valve disk 2 and the bottom end surface of the intake valve disk 2 is preferably designed to be a smooth curved surface. Become the smooth curved surface and be convenient for the air current direction more through designing into, it is that to explain, smooth curved surface specifically can be for forming in the fillet of linking up the position, also be the indent arcwall face, and in order to adapt to different models and design demand, the fillet radius R of this indent arcwall face specifically can select to satisfy the relation: r is more than 0 and less than or equal to 0.05D; or R is more than 0 and less than or equal to 0.1D; or R is more than 0 and less than or equal to 0.2D, wherein D is the diameter of the bottom end face of the air inlet valve disc of the air inlet valve. In the practical application process, corresponding design parameters can be selected according to specific models and design requirements.

In some specific embodiments, the limiting portion is a limiting protrusion or a limiting groove provided on the outer periphery of the intake valve stem 1. The valve guide pipe is a component which is arranged in the cylinder cover and used for guiding the reciprocating motion of the valve, in order to limit the relative rotation between the intake valve and the valve guide pipe, the invention can be provided with a limit guide strip or a limit channel in the valve guide pipe, the extending directions of the limit guide strip and the limit channel are both parallel to the axis of the intake valve rod 1, correspondingly, the periphery of the intake valve rod 1 is provided with a limit part which is in sliding fit with the intake valve rod, and the limit part can be specifically designed into a limit groove or a limit bulge. Of course, the outer peripheral surface of the intake valve rod 1 may also be designed as a non-rotational body cylindrical surface such as an elliptic cylindrical surface or a prismatic surface, that is, the cross section of the intake valve rod 1 is a non-circular structure, and correspondingly, the inner hole of the valve guide is designed as an elliptic hole or a polygonal hole structure matched with the inner hole, so that the arrangement can also play a role in limiting the relative rotation of the intake valve and the valve guide.

In addition, the invention also provides a cylinder cover, which is applied to a gas engine reformed on the basis of a diesel engine and comprises an air inlet throat 4 and an air outlet throat, wherein an air inlet valve seat ring 6 and an air inlet valve used for realizing the on-off control of air inlet by matching with the air inlet valve seat ring 6 are arranged in the air inlet throat 4, and the air inlet valve is the air inlet valve described in any scheme. Since the intake valve has the technical effects, the cylinder head with the intake valve also has the corresponding technical effects, and the detailed description is omitted.

It should be noted that, as will be understood by those skilled in the art, an engine cylinder head generally has an intake passage 10 and an exhaust passage, the intake passage and the exhaust passage are respectively located at two sides of the length direction of the cylinder head, and the intake passage is responsible for organizing the airflow during the intake process of the engine

In a further embodiment, the intake valve structure has a cylinder head that can be applied to two intake valves and two exhaust valves, wherein the intake throat 4 includes a first intake throat 41 and a second intake throat 42, intake valves are installed in both the first intake throat 41 and the second intake throat 42, and the exhaust throat 5 includes a first exhaust throat 51 disposed opposite to the first intake throat 41 and a second exhaust throat 52 disposed opposite to the second intake throat 42.

In further embodiments, the first inlet throat 41 is aligned withThe included angle between the connecting line of the center of the corresponding intake valve and the center of the flow blocking convex part 3 on the intake valve disc of the corresponding intake valve and the axis 7 of the crankshaft is theta₁The included angle between the connecting line of the inlet valve center corresponding to the first inlet throat 41 and the exhaust valve center corresponding to the first exhaust throat 51 and the axis 7 of the crankshaft is theta₂Theta for achieving better tumble effect and meeting different models and design requirements₁And theta₂The following relationship can be specifically selected: theta is not less than 0₁≤2θ₂(ii) a Or 0.5 theta₂≤θ₁≤1.5θ₂(ii) a Or 0.8 theta₂≤θ₁≤1.2θ₂(ii) a Or 0.9 theta₂≤θ₁≤1.1θ₂。

Similarly, the included angle between the connecting line of the center of the inlet valve corresponding to the second inlet throat 42 and the center of the flow blocking convex part 3 on the inlet valve disc of the inlet valve corresponding to the second inlet throat and the axis 7 of the crankshaft is theta₃The included angle between the connecting line of the inlet valve center corresponding to the second inlet throat 42 and the exhaust valve center corresponding to the second outlet throat 52 and the axis 7 of the crankshaft is theta₄Theta for achieving better tumble effect and meeting different models and design requirements₃And theta₄The following relationship can be specifically selected: theta is not less than 0₃≤2θ₄(ii) a Or 0.5 theta₄≤θ₃≤1.5θ₄(ii) a Or 0.8 theta₄≤θ₃≤1.2θ₄(ii) a Or 0.9 theta₄≤θ₃≤1.1θ₄。

It should be noted that, as will be understood by those skilled in the art, in the two-intake and two-exhaust cylinder head, the first intake throat 41 communicates with the head intake port 13 outside the cylinder head through the first intake passage 11 in the cylinder head, and the second intake throat 42 communicates with the head intake port 13 through the second intake passage 12 in the cylinder head, wherein the first intake passage 11 and the second intake passage 12 are mainly used for guiding the air flow. A first air inlet valve seat ring 61 is arranged in the first air inlet throat 41 and is used for being matched with an air inlet valve to open and close so as to realize the on-off control of air inlet; the second inlet throat 42 is internally provided with a second inlet valve seat ring 62 which is used for matching with the corresponding inlet valve to open and close so as to realize the on-off control of the inlet air.

Furthermore, in general, for diesel engines, the line connecting the centers of the two intake valves and the center of the engine crankshaft forms an angle α, which inevitably results in one of the two intake valves being at a smaller distance from the intake side and the other valve being at a greater distance from the intake side. Because the distances from the intake valve to the intake side are different, the intake passage close to the intake side is generally designed to be shorter and thicker, and because the space of the intake passage is limited, the tumble ratio is limited by only changing the shape of the inner wall of the intake passage to increase the tumble ratio.

Therefore, for a two-intake and two-exhaust cylinder head, the present invention is preferably designed as shown in fig. 7, wherein the intake valve retainer 6 includes a first intake valve retainer 61 disposed in the first intake throat 41 and a second intake valve retainer 62 disposed in the second intake throat 42, and the height H of the first intake valve retainer 61 from the bottom surface of the cylinder head₁Is greater than the height H of the second intake valve seat ring 62 from the bottom surface of the cylinder head₂. Because two last hedging air currents of (air) intake valve central line side are the asymmetric structure of one on the other, compare in the mode that two traditional (air) intake valve seat rings symmetrical arrangement, can effectively reduce two ascending air current hedging interferences of (air) intake valve central line side, then reduce the air current kinetic energy loss, be favorable to promoting the tumble flow effect in the combustion chamber more. In addition, the arrangement can maximally improve the flow capacity of the air passage on the premise of ensuring the tumble ratio of the air passage. The basic principle is that the height of the first intake valve seat ring 61 relative to the bottom surface of the cylinder head is higher, so that the flow guiding length of a guiding wall below the first intake valve seat ring 61 can be further prolonged in the opening process of the first intake valve, and tumble flow is more favorably generated. Meanwhile, due to the guiding of the air flow through the guide wall, and as the first intake valve seat ring is increased, when the intake valve is opened, the valve disc corresponding to the intake valve is closer to the bottom surface of the cylinder cover, so that the air flow is more favorable for moving towards a target direction (towards the direction of the first exhaust throat 51), and meanwhile, the air flow interference in the direction of the central connecting line of the two intake valves is reduced. Wherein the guide below the air inlet raceThe flow structure may be embodied in such a manner that a first inlet chamfer 81 is formed below the first inlet throat 41 corresponding to the first inlet retainer 61, and a second inlet chamfer 82 is formed below the second inlet throat 42 corresponding to the second inlet retainer 62.

In particular embodiments, the height H of the first intake valve seat insert 61 from the bottom surface of the cylinder head₁Height H from the bottom surface of the cylinder head to the second intake valve seat ring 62₂Height difference H of₃Specifically, the relationship: h is more than 0₃And D is not more than 0.2D, wherein D is the diameter of the bottom end face of the intake valve disc of the intake valve arranged at the first intake valve seat ring 61, or the diameter of the bottom end face of the intake valve disc of the intake valve arranged at the second intake valve seat ring 62. H is found by simulation test₃The above relationship is set, so that a good tumble effect can be generated in most engine models.

It is understood that the above relation is only the preferred value taking mode given by the invention after the simulation of the mainstream engine model, and in the practical application process, other corresponding value taking ranges, such as H, can be selected according to the specific engine model₃The selection and meeting relationship can also be selected according to the configuration requirements of different machine types as follows: h is more than 0₃Less than or equal to 1 mm; or 0 < H₃Less than or equal to 2 mm; or 0 < H₃Less than or equal to 3 mm; or 0 < H₃Less than or equal to 4 mm; or 0 < H₃Less than or equal to 5 mm; or 0 < H₃Less than or equal to 6mm, and the like. In the practical application process, the selection can be performed according to the practical requirements, and is not specifically limited herein.

In some specific embodiments, the first air inlet chamfer 81 and the second air inlet chamfer 82 may be designed as follows: the center of the first air inlet chamfer 81 is offset by a first preset distance towards the first exhaust throat 51 relative to the center of the first air inlet throat 41; the center of the second inlet chamfer 82 is offset a second predetermined distance toward the second exhaust throat 52 relative to the center of the second inlet throat 42. Because the first/second air inlet chamfers have obvious flow guiding effect, the first air inlet chamfers 81 are designed to be deviated towards the direction of the first exhaust throat 51, so that the width of a gap on one side close to the first exhaust throat 51 is larger, most of the air flow enters the air cylinder from the gap on one side close to the first exhaust throat 51, the air flow on one side far away from the first exhaust throat 51 is reduced, and the air flows on the two sides are easier to form large-scale tumble motion after entering the air cylinder. Similarly, the second inlet chamfer 82 is designed to be offset toward the second exhaust throat 52, which has similar effects and will not be described herein.

Therefore, on the basis of the existing diesel engine, the first/second air inlet chamfers are designed into the eccentric chamfers, so that the effective diversion of the air inlet flow is realized, the tumble strength is favorably enhanced, the turbulent flow is favorably formed at the last stage of compression, and the heat efficiency of the gas engine is improved.

It should be noted that, in the practical application process, the first preset distance and the second preset distance may be designed to be equal or unequal, and may be selected according to the practical requirements.

In addition, the first air intake chamfer 81 and the second air intake chamfer 82 may be both a rotary chamfer or a non-rotary chamfer, and may be selected according to actual requirements during practical application.

In a further embodiment, the chamfer structure with different longitudinal section shapes can be obtained according to different rotary processing surfaces, for example, after the cylinder cover material is removed by adopting a conical rotary processing surface, the longitudinal section of the guide wall surface of the chamfer structure is in a linear structure. In practical application, the longitudinal section of the guide wall surface of the chamfer structure can be a straight line or a curve.

Further, the longitudinal section of the guide wall surface of the chamfer structure is preferably a curve protruding towards the inner direction of the cylinder, and in the scheme, the chamfer surface protruding towards the inner side of the cylinder can prevent airflow from flowing and separating when the airflow passes through the chamfer, so that the tumble effect of the airflow is improved.

It should be noted that the rotation center line of the first air inlet chamfer 81 may be arranged in parallel or inclined with respect to the axis of the first air inlet throat 41; similarly, the center line of revolution of the second inlet chamfer 82 may be arranged parallel to the axis of the second inlet throat 42 or may be arranged obliquely. In the practical application process, the air inlet chamfering device can be configured according to specific requirements, and the first air inlet chamfering and the second air inlet chamfering are preferably arranged in the same arrangement mode.

For example, the center line of revolution of the first inlet chamfer 81 is arranged obliquely with respect to the axis of the first inlet throat 41 and the lower end opening of the first inlet chamfer 81 is arranged toward the corresponding first outlet throat 51; likewise, the centerline of revolution of the second inlet chamfer 82 is disposed obliquely to the axis of the second inlet throat 42 and the lower end opening of the second inlet chamfer 82 is disposed toward its corresponding second exhaust throat 52. By the arrangement, a wider chamfer surface can be processed at the edge of one side of the air inlet throat close to the exhaust throat, and meanwhile, the transition between the chamfer surface at the side and the bottom surface of the cylinder cover and the wall surface of the air inlet throat is smoother, so that the kinetic energy loss of airflow flowing through the air inlet chamfer is reduced.

The inclination angle of the gyration center line of the first air inlet chamfer relative to the axis of the first air inlet throat and the inclination angle of the gyration center line of the second air inlet chamfer relative to the axis of the second air inlet throat can be designed to be equal or different. In a further embodiment, the setting of the selectable value range of the inclination of the rotation center line of the first air inlet chamfer 81 relative to the axis of the first air inlet throat 41 is different for different engine models, for example, the selectable value range may be 0 to 30 degrees, or 0 to 20 degrees, or 0 to 10 degrees, or 0 to 5 degrees; similar to the inclination angle of the rotation center line of the first air inlet chamfer, the rotation center line of the second air inlet chamfer 82 is set in an optional value range of 0-30 degrees, 0-20 degrees, 0-10 degrees or 0-5 degrees relative to the inclination angle of the axis of the second air inlet throat 42.

It should be noted that the first air inlet chamfer 81 and the second air inlet chamfer 82 can be designed to have the same structure and size; the structure and the size of the device can be designed to be different, and the device can be selected according to actual requirements in the actual application process. For example, in the structural form that the length of the guide wall surface of the first air inlet chamfer 81 is greater than that of the guide wall surface of the second air inlet chamfer 82, when the distance between the first air inlet throat 41 and the cylinder head air inlet is smaller than that between the second air inlet throat 42 and the cylinder head air inlet, the arrangement is favorable for increasing the diversion length, so that the tumble flow is more favorably generated.

In some specific embodiments, a side of the intake valve seat ring 6 far away from the exhaust throat is provided with a tumble sharp corner 9, an axial projection of the tumble sharp corner 9 on the upper end surface of the intake valve seat ring 6 is a sharp corner projection, the sharp corner projection forms a convex area which is protruded from the inner side edge of the intake valve seat ring 6 to the center of the intake valve seat ring 6 along the radial direction, and the width of the projection of the sharp corner on the middle part along the circumferential direction of the intake valve seat ring 6 is larger than the width of the two ends.

The working principle of adopting the tumble sharp angle is as follows:

when an engine cylinder inhales air, an inlet valve is opened, as shown in fig. 8, inlet airflow enters the cylinder from a gap between an inlet valve seat ring 6 and the inlet valve, and tumble sharp corners 9 arranged on the inner side of the inlet valve seat ring 6 enable the inlet airflow to be extruded and cast towards the direction of an exhaust throat, so that most of the inlet airflow enters the cylinder from the gap close to one side of the exhaust throat, the airflow far away from one side of the exhaust throat is reduced, and the airflows on the two sides more easily form large-scale tumble motion after entering the cylinder.

On the basis of the existing diesel engine, the tumble sharp corner 9 structure is arranged in the intake valve seat ring 6, so that intake airflow can be cast towards the exhaust throat when passing through the intake valve seat ring 6, the tumble strength in an air cylinder is enhanced, turbulent flow is formed in the last stage of compression, and the heat efficiency of a gas engine is improved.

The tumble flow cusp 9 in this embodiment may be formed integrally with the intake valve seat ring 6 by, for example, integral casting, forging, machining, or the like. By processing the tumble sharp corner 9 on the inner wall of the intake valve seat ring 6 on the side far away from the exhaust throat, the guide projection effect of the intake airflow at the tail end of the intake path can be realized, so that the intake airflow is guided to the exhaust side to the maximum extent, and the tumble motion is favorably formed in the cylinder.

It should be noted that the tumble sharp corner 9 in this embodiment functions to extrude most of the intake air flow toward the exhaust throat before the intake air flow is injected into the cylinder, and the tumble sharp corner 9 capable of achieving the above function may be designed in various structural shapes, for example, one side edge of the tumble sharp corner 9 facing the center of the intake valve seat ring 6 is designed in an arc shape, a straight shape, a fold shape, or other curved structures. Preferably, the projection of the cusp in this solution is a crescent shaped area, and the concave side of the crescent shaped area is arranged towards the center of the intake valve seat insert 6, i.e. one side edge of the tumble cusp 9 towards the center of the intake valve seat insert 6 is designed as a concave arc.

Preferably, the edge of the sharp angle projection facing to one side of the center of the intake valve seat ring 6 is a sharp angle characteristic line, the connecting line of the midpoint of the sharp angle characteristic line and the center of the intake valve seat ring 6 is a sharp angle direction line, the included angle between the sharp angle direction line and the axis of the crankshaft is a sharp angle direction angle, and the included angle between the connecting line of the center of the intake throat and the center of the exhaust throat and the axis of the crankshaft is an intake and exhaust throat connecting line direction angle. In one particular embodiment, the cylinder head has two intake valve seats and two exhaust valve seats, each of which may have a tumble tip angle disposed as shown in FIG. 9.

In addition, an included angle between a connecting line of the center of the first inlet valve seat ring (namely the center of the first inlet throat) and the center of the first exhaust valve seat ring (namely the center of the first exhaust throat) and the axis of the crankshaft is a first inlet and exhaust throat connecting direction angle, an included angle between a connecting line of the center of the second inlet valve seat ring (namely the center of the second inlet throat) and the center of the second exhaust valve seat ring (namely the center of the second exhaust throat) and the axis of the crankshaft is a second inlet and exhaust throat connecting direction angle, an included angle between a connecting line of a midpoint of a sharp corner characteristic line in the first inlet valve seat ring and the center of the first inlet valve seat ring and the axis of the crankshaft is a first sharp corner direction angle, and an included angle between a connecting line of a midpoint of a sharp corner characteristic line in the second inlet valve seat ring and the center of the second inlet valve seat ring and the axis of the crankshaft is a second sharp corner direction angle, preferably, the inlet and exhaust throat connecting direction angle is 0-2 times or 0.5 times or 0.8 times or 1.2 times or 0.1.2 times or 0.9 times or 1.1 times of the sharp corner direction angle.

Preferably, as shown in fig. 8, the tumble flow cusp 9 is at a minimum distance L from the centerline of the intake valve seat ring 6 (intake valve seat ring centerline)₀For the inlet valve seat ring inner diameter D₀(minimum diameter of inlet valve seat ring 2 and inlet valve sealing conical surface) 0-0.1 times, 0-0.2 times, 0-0.3 times, 0-0.4 times, 0-0.5 times, distance H between tumble sharp angle 4 and cylinder head bottom surface 3₀For the inlet valve seat ring inner diameter D₀0 to 0.5 times or 0 to 0.8 times or 0 to 1 times or 0 to 1.5 times or 0 to 2 times or 0 to 2.5 times or 0 to 3 times of the total amount of the component (B).

It should be noted that the tumble flow sharp corner 9 specifically includes an upper side flow guide surface and a lower side processing surface, the juncture of the upper side flow guide surface and the lower side processing surface is the edge of the tumble flow sharp corner 9 protruding toward the center of the intake valve seat ring 6, the tumble flow sharp corner 9 may be designed into different structures, and the lower side processing surface may be specifically designed into a rotary processing surface, or a plurality of planes connected in sequence, or other curved surface structures, and the like. Preferably, in the scheme, the lower side processing surface of the tumble sharp corner 9 is a rotary processing surface surrounding a processing axis, the processing axis can be designed to be superposed, parallel or relatively obliquely arranged with the central line of the intake valve seat ring, and the generatrix of the rotary processing surface is a straight line, a broken line or a curve.

It should be noted that, according to different generating line shapes, the above-mentioned rotary processing surface can be designed into various different conical surface structures, preferably, the rotary processing surface in this scheme is a conical processing surface, the processing axis of the conical processing surface coincides with the intake valve seat ring axis, and the vertex of the conical processing surface is located above the intake valve seat ring. The specific shape of the tumble angle 9 depends on the size of the cone angle of the conical processing surface, and the tumble angle 9 is sharper when the cone angle is larger. Preferably, the value range of the cone angle of the conical processing surface in the scheme is 60-160 degrees, and within the range, the tumble sharp angle 9 can be ensured to have a sharp enough angle, so that the flow velocity mutation and the extrusion effect on the intake air flow are further strengthened.

In a further embodiment, the cylinder head air inlet can be specifically arranged on the side face or the top face or the bottom face of the cylinder head, and in the practical application process, the air inlet can be selectively arranged according to the practical requirements, so that the installation and arrangement of engines of different models can be realized.

In addition, the invention also provides a gas engine, which comprises a cylinder cover, wherein the cylinder cover is the cylinder cover described in any scheme, and the cylinder cover has the technical effects, so that the gas engine with the cylinder cover also has the corresponding technical effects, and the details are not repeated.

The intake valve, the cylinder head and the gas engine provided by the present invention have been described in detail. It should be noted that, in the present specification, the embodiments are all described in a progressive manner, each embodiment focuses on differences from other embodiments, and the same and similar parts among the embodiments may be referred to each other.

It is also noted that, in this document, terms such as "comprises," "comprising," or any other variation thereof, are intended to cover a non-exclusive inclusion, such that an article or apparatus that comprises a list of elements does not include only those elements but may include other elements not expressly listed or inherent to such article or apparatus. Without further limitation, an element defined by the phrase "comprising an … …" does not exclude the presence of other like elements in an article or device that comprises the element.

The principles and embodiments of the present invention are explained herein using specific examples, which are presented only to assist in understanding the core concepts of the present invention. It should be noted that, for those skilled in the art, it is possible to make various improvements and modifications to the present invention without departing from the principle of the present invention, and those improvements and modifications also fall within the scope of the claims of the present invention.