1. The cylinder cover comprises at least two air inlet throats, and an air inlet valve seat ring is arranged in each air inlet throat.

2. The cylinder cover of claim 1, wherein an edge of the flow guide protrusion facing the side of the center line of the intake valve seat ring is a flow guide protrusion edge, the flow guide protrusion comprises an upper flow guide inclined surface extending downwards from the upper end surface of the intake valve seat ring to the flow guide protrusion edge and a lower flow guide inclined surface extending downwards from the flow guide protrusion edge to the sealing conical surface of the intake valve seat ring, and an intersection line of the flow guide protrusion edge and the longitudinal section of the intake valve seat ring is an arc line.

3. The cylinder head according to claim 2, wherein the axial projection of the flow guide protrusion edge on the bottom surface of the cylinder head is a flow guide protrusion characteristic line, the flow guide protrusion characteristic line is a straight line, the projection of the crankshaft axis on the bottom surface of the cylinder head is a crankshaft axis direction line, the straight line direction which is located on the bottom surface of the cylinder head and is perpendicular to the crankshaft axis direction line is a reference direction, the included angle between the flow guide protrusion characteristic line and the reference direction is a flow guide protrusion characteristic angle, and the flow guide protrusion characteristic angle is 60-120 °.

4. The cylinder head of claim 3, wherein a minimum distance of the guide lobe feature line from the intake valve seat insert centerline is greater than 0 and equal to or less than 0.5 times an outer diameter of the intake valve seat insert.

5. The cylinder head according to claim 3, wherein an angle between a line connecting centers of two adjacent intake throats and an axial line of the crankshaft is 60 ° to 90 °.

6. The cylinder head of claim 2, wherein the upper deflector ramp is angled 30 ° -60 ° from the upper end surface of the intake valve seat insert, and the lower deflector ramp is angled 30 ° -60 ° from the lower end surface of the intake valve seat insert.

7. The cylinder head of claim 2, wherein the radius of the circular arc line is equal to or less than 0.2 times the outer diameter of the intake valve seat insert.

8. The cylinder head of claim 2, wherein a distance between a center of the circular arc line and an upper end surface of the intake valve seat ring is equal to or less than 0.2 times an outer diameter of the intake valve seat ring.

9. The cylinder cover according to any one of claims 1 to 8, wherein each branch intake passage where the intake throat is located is further provided with a tumble generation sharp corner, the tumble generation sharp corner is located on one side wall surface of the branch intake passage away from the exhaust throat and above the intake valve seat ring, and the tumble generation sharp corner protrudes towards the center line of the intake valve seat ring relative to the wall surface of the branch intake passage.

10. The cylinder head according to claim 9, wherein an axial projection of the tumble flow-generating sharp angle on the upper end surface of the intake valve seat ring is a sharp-angle projection which is a convex region that protrudes from an inner edge of the intake valve seat ring in a radial direction toward a center of the intake valve seat ring, and a width of the sharp-angle projection is larger at a middle portion in a circumferential direction of the intake valve seat ring than at both ends thereof.

11. The cylinder head of claim 10, wherein the pointed projection is a crescent shaped region with the concave side disposed toward the center of the intake valve seat insert.

12. The cylinder head of claim 9, wherein the minimum distance of the tumble flow-generating tip angle to the intake valve seat ring centerline is greater than 0 and equal to or less than 0.5 times the minimum diameter of the sealing cone surface of the intake valve seat ring.

13. A gas engine, characterized by comprising a cylinder head according to any one of claims 1 to 12.

Background

With the development of gas engine technology, more and more engine manufacturers are beginning to design and develop gas engines on the basis of diesel engines. Due to the particularity of the combustion mode of the diesel engine, an air inlet passage in the cylinder head of the engine is required to organize the air flow to generate a sufficient swirl ratio in the process of air intake. However, gas engines do not require excessive swirl, but rather, require more tumble flows that organize the gas flow to create a center axis of rotation perpendicular to the center axis of the liner. That is, for a gas engine, the purpose of optimizing combustion can only be achieved if sufficient tumble flow is effectively generated.

For a four-valve engine, in the prior art, a region below a cylinder head between two intake valves 02 is a region where high-speed jets flowing out through two intake passage branches collide with each other, that is, two intake airflows interfere with each other in the region, and a synthesized high-speed jet region 01 swings back and forth, as shown in fig. 1, the directions of the intake airflows corresponding to a time a, a time b and a time c are different, so that the flow energy of the intake airflows is greatly lost, the maintenance of large-scale tumble motion is not facilitated, and at the end of a compression stroke, the large-scale flow is broken into small-scale flow, so that turbulent kinetic energy is at a lower level, and the effect of accelerating combustion is hardly achieved.

Therefore, how to avoid the mutual interference of the intake air flows and maintain the intake energy is a technical problem that needs to be solved by those skilled in the art at present.

Disclosure of Invention

In view of the above, the present invention provides a cylinder head and a gas engine, and the cylinder head and the gas engine are based on the existing diesel engine cylinder head structure, and through structural improvement, the cylinder head can avoid air flow interference in the middle area of two intake valves, maintain high intake energy, and facilitate maintaining large-scale tumble motion, thereby facilitating rapid combustion of the gas engine.

In order to achieve the purpose, the invention provides the following technical scheme:

the cylinder cover comprises at least two air inlet throat openings, wherein an air inlet valve seat ring is arranged in each air inlet throat opening, and a flow guide bulge protruding towards the central line of the air inlet valve seat ring is arranged on the inner wall of each air inlet valve seat ring at a position close to the adjacent air inlet valve seat ring.

Preferably, the protruding orientation of water conservancy diversion the edge of (air) intake valve seat circle central line one side is the water conservancy diversion bellying edge, the water conservancy diversion is protruding include by the up end downwardly extending of (air) intake valve seat circle goes up the water conservancy diversion inclined plane of (air) intake valve seat circle and by the water conservancy diversion bellying edge downwardly extending reaches the lower water conservancy diversion inclined plane of the sealed conical surface of (air) intake valve seat circle, the water conservancy diversion bellying edge with the intersecting line of the longitudinal section of (air) intake valve seat circle is the circular arc line.

Preferably, the axial projection of the flow guide protrusion edge on the bottom surface of the cylinder cover is a flow guide protrusion characteristic line, the flow guide protrusion characteristic line is a straight line, the projection of the crankshaft axis on the bottom surface of the cylinder cover is a crankshaft axis direction line, the straight line direction which is located on the bottom surface of the cylinder cover and perpendicular to the crankshaft axis direction line is a reference direction, the included angle between the flow guide protrusion characteristic line and the reference direction is a flow guide protrusion characteristic angle, and the flow guide protrusion characteristic angle is 60-120 degrees.

Preferably, the minimum distance from the flow guide convex characteristic line to the central line of the inlet valve seat ring is greater than 0 and less than or equal to 0.5 times of the outer diameter of the inlet valve seat ring.

Preferably, the included angle between the connecting line of the centers of two adjacent air inlet throats and the axial line of the crankshaft is 60-90 degrees.

Preferably, the included angle between the upper diversion inclined plane and the upper end face of the inlet valve seat ring is 30-60 degrees, and the included angle between the lower diversion inclined plane and the lower end face of the inlet valve seat ring is 30-60 degrees.

Preferably, the radius of the circular arc line is equal to or less than 0.2 times the outer diameter of the intake valve seat ring.

Preferably, the distance between the circle center of the arc line and the upper end face of the intake valve seat ring is less than or equal to 0.2 time of the outer diameter of the intake valve seat ring.

Preferably, every the branch intake duct at intake throat place still is equipped with the tumble and generates the closed angle, the tumble generates the closed angle and is located a lateral wall face that the branch intake duct kept away from the exhaust throat and is located the top of intake valve seat circle, the tumble generates the closed angle relative the wall of branch intake duct to intake valve seat circle central line protrusion.

Preferably, an axial projection of the tumble flow generation sharp corner on the upper end surface of the intake valve seat ring is a sharp corner projection, the sharp corner projection is a convex region which is protruded from the inner side edge of the intake valve seat ring to the center of the intake valve seat ring along the radial direction, and the width of the middle part of the sharp corner projection in the circumferential direction of the intake valve seat ring is greater than the width of the two ends of the sharp corner projection.

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

Preferably, the minimum distance from the tumble flow generating tip angle to the intake valve seat ring centerline is greater than 0 and equal to or less than 0.5 times the minimum diameter of the sealing taper surface of the intake valve seat ring.

The cylinder cover provided by the invention comprises at least two air inlet throat openings, each air inlet throat opening is internally provided with an air inlet valve seat ring, and the inner wall of each air inlet valve seat ring is provided with a flow guide bulge protruding towards the central line of the air inlet valve seat ring at a position close to the adjacent air inlet valve seat ring.

The working principle of the invention is as follows:

when the engine cylinder breathes in, the intake valve is opened, the air current of admitting air gets into in the cylinder by the gap between intake valve seat circle and the intake valve, the water conservancy diversion arch that the intake valve seat circle inboard set up forces the air current of admitting air to flow towards the direction of keeping away from adjacent intake valve seat circle, namely, most air current flows from other regional flows of intake valve seat circle hoop, and the air current proportion of two intake valve seat circles middle zone is then greatly reduced, can avoid two intake valve middle zone's air current interference like this, thereby make the air current of admitting air maintain higher energy of admitting air, be favorable to maintaining large-scale tumble motion, promote turbulent kinetic energy more easily at compression stroke's final stage, and then be favorable to gas engine's fast combustion.

Therefore, on the basis of the cylinder cover structure of the existing diesel engine, the intake valve seat ring structure is only changed, so that the mutual interference of intake air flow can be avoided, the intake energy can be maintained, the purpose of optimizing combustion is achieved, the change cost is extremely low, and the feasibility is high.

The cylinder cover provided by the invention has the following beneficial effects:

1) the invention has higher feasibility and reduces the modification cost;

2) according to the invention, the flow guide bulges are designed on the inner wall of the inlet valve seat ring, and the arrangement structure of the adjacent flow guide bulges is reasonably arranged, so that the airflow collision is avoided, and the energy loss is reduced;

3) the invention also designs the characteristic of generating sharp angles by tumble flow in the branch air inlet channel, thereby further guiding the air flow to the exhaust side, being beneficial to generating large-scale tumble motion in the cylinder and being beneficial to improving the turbulent kinetic energy at the final stage of compression.

The invention also provides a gas engine comprising the cylinder cover. The derivation process of the beneficial effects generated by the gas engine is substantially similar to the derivation process of the beneficial effects brought by the cylinder cover, and therefore, the description is omitted.

Drawings

In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings used in the description of the embodiments or the prior art will be briefly described below, it is obvious that the drawings in the following description are only some embodiments of the present invention, and for those skilled in the art, other drawings can be obtained according to the drawings without creative efforts.

FIG. 1 is a schematic view of the prior art of high velocity inlet jet impingement at various times;

FIG. 2 is a longitudinal cross-sectional schematic view of a cylinder head in an embodiment of the invention;

FIG. 3 is a schematic structural diagram of an intake valve seat insert and a guide protrusion thereof according to an embodiment of the present invention;

FIG. 4 is a schematic view of a feature angle of a guide protrusion in an embodiment of the invention;

FIG. 5 is a schematic view of the location of the inlet throat in an embodiment of the present invention;

FIG. 6 is a schematic longitudinal cross-sectional view of an intake valve seat insert and flow guide projections thereof in an embodiment of the invention;

FIG. 7 is a schematic view of the shape of a pointed projection in an embodiment of the present invention;

FIG. 8 is a graph comparing the airway flow coefficient of the present invention and the prior art;

fig. 9 is a graph comparing the tumble ratio of the present solution with the prior solution.

The meaning of the various reference numerals in figures 1 to 7 is as follows:

01-high speed jet area, 02-inlet valve;

the method comprises the following steps of 1-inlet valve seat ring, 2-tumble generation sharp angle, 3-inlet valve seat ring central line, 4-cylinder, 5-guide bulge, 6-guide bulge characteristic line, 7-inlet valve seat ring center, 8-reference direction, 9-crankshaft axis direction line, 10-inlet throat, 11-inlet throat center connecting line, 12-exhaust throat, 13-arc line, 14-upper guide inclined plane, 15-lower guide inclined plane, 16-sealing conical surface, 17-inlet valve seat ring upper end surface and 18-sharp angle projection.

Detailed Description

The technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the drawings in the embodiments of the present invention, and it is obvious that the described embodiments are only a part of the embodiments of the present invention, and not all of the 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 invention.

Referring to fig. 2 to 7, fig. 2 is a longitudinal sectional view of a cylinder head according to an embodiment of the present invention; FIG. 3 is a schematic structural diagram of an intake valve seat insert and a guide protrusion thereof according to an embodiment of the present invention; FIG. 4 is a schematic view of a feature angle of a guide protrusion in an embodiment of the invention; FIG. 5 is a schematic view of the location of the inlet throat in an embodiment of the present invention; FIG. 6 is a schematic longitudinal cross-sectional view of an intake valve seat insert and flow guide projections thereof in an embodiment of the invention; FIG. 7 is a schematic view of the shape of a pointed projection in an embodiment of the present invention.

In order to solve the problems of the existing gas engine, the invention provides a cylinder cover for the gas engine, the cylinder cover is combined with the existing weak tumble fast combustion system for use, and the tumble stability in the cylinder can be further improved, wherein the weak tumble fast combustion system refers to the cylinder cover in the invention patent (a weak tumble fast combustion system and a gas engine, publication number CN 111287860A), the cylinder cover structure is formed by reforming the cylinder cover of the diesel engine, the top surface of a combustion chamber formed by the cylinder cover is a flat-top structure, namely, a valve rod of the cylinder cover is arranged along the axial direction of a piston, an air inlet channel of the cylinder cover is a weak tumble air channel, specifically, the air inlet channel of the cylinder cover can enable intake air flow to generate large-scale weak tumble motion in the cylinder, and specific weak tumble structure design characteristics are not repeated herein.

The cylinder cover provided by the invention comprises at least two air inlet throat openings 10, wherein an air inlet valve seat ring 1 is arranged in each air inlet throat opening 10, and a flow guide bulge 5 protruding towards the central line 3 of the air inlet valve seat ring is arranged on the inner wall of each air inlet valve seat ring 1 at a position close to the adjacent air inlet valve seat ring 1.

The working principle of the invention is as follows:

when the engine cylinder breathes in, the intake valve is opened, the air current of admitting air gets into in the cylinder 4 by the gap between intake valve seat insert 1 and the intake valve, the air current of admitting air is forced to flow to the direction of keeping away from adjacent intake valve seat insert 1 to the water conservancy diversion arch 5 that the intake valve seat insert 1 inboard set up, namely, most air current flows from other regional flows of intake valve seat insert 1 hoop, and the air current proportion of two intake valve seat inserts 1 middle zone is then greatly reduced, can avoid two regional air current interferences in intake valve middle like this, thereby make the air current of admitting air maintain higher energy of admitting air, be favorable to maintaining the motion of large-scale tumble, promote turbulent kinetic energy more easily at last stage of compression stroke, and then be favorable to gas engine's fast combustion.

Referring to fig. 8, compared with the prior art (i.e. the prior art does not design a cylinder head with a flow guide protrusion on an intake valve seat ring), in the stage of small valve lift, because the intake airflow is mainly sucked into the cylinder from the annular gap between the intake valve and the intake valve seat ring 1 by the negative pressure, and the flow guide protrusion 5 structure is designed on the inner wall of the intake valve seat ring 1, the flow area of the airflow is reduced compared with the prior art, and therefore, the flow coefficient of the scheme in the stage of small valve lift is lower than that of the prior art; at big valve lift stage, the effect of negative pressure weakens in the jar, the air current mainly gets into in the jar by flow inertia, because there is high-speed efflux between two (air) intake valves to collide the region in the current scheme, consequently, this collide regional energy of admitting air that has weakened some air currents, and then lead to whole flow coefficient to diminish, this scheme guides most air currents to flowing along other regions of (air) intake valve circumference through the protruding 5 structure of water conservancy diversion, owing to avoid two (air) intake valve middle zone's clash interference, consequently make most air currents can flow into the jar from other clearances of circumference more steadily, and then kept higher energy of admitting air, the flow coefficient of final performance is higher than current scheme. Referring to fig. 9, compared with the prior art, in the process that the valve lift is changed from small to large, because the scheme always avoids the collision and interference of the air flow in the middle area of the two intake valves from small, the tumble motion formed by the intake air flow in the cylinder can be kept stable and the strength is gradually strengthened.

Therefore, on the basis of the cylinder cover structure of the existing diesel engine, the structure of the intake valve seat ring 1 is changed, so that the mutual interference of intake air flow can be avoided, and the intake energy can be maintained, thereby achieving the purpose of optimizing combustion, and having extremely low modification cost and high feasibility.

Preferably, the edge of the flow guide protrusion 5 towards one side of the central line 3 of the intake valve seat ring is a flow guide protrusion edge, the flow guide protrusion 5 comprises an upper flow guide inclined plane 14 extending downwards from the upper end surface of the intake valve seat ring 1 (i.e. the upper end surface 17 of the intake valve seat ring in fig. 6) to the flow guide protrusion edge and a lower flow guide inclined plane 15 extending downwards from the flow guide protrusion edge to the sealing conical surface 16 of the intake valve seat ring 1, and the intersection line of the flow guide protrusion edge and the longitudinal section of the intake valve seat ring 1 is an arc line 13. The upper guide ramp 14 serves to guide the air flow into the central through-hole of the inlet valve seat insert 1. In the scheme, the longitudinal section of the edge of the flow guide bulge is designed into an arc line 13, namely, the joint of the lower end of the upper flow guide inclined plane 14 and the upper end of the lower flow guide inclined plane 15 is designed into a transitional fillet structure, so that the air flow is smoothly transited to the lower flow guide inclined plane 15, and the flow resistance is further reduced. The lower guide slope 15 is used for guiding the air flow to the sealing conical surface 16, so that the air flow can smoothly pass through the gap between the inlet valve seat ring 1 and the inlet valve when the inlet valve is opened.

Preferably, the axial projection of the flow guide protrusion edge on the bottom surface of the cylinder cover is a flow guide protrusion characteristic line 6, the flow guide protrusion characteristic line 6 is preferably a straight line, the projection of the crankshaft axis on the bottom surface of the cylinder cover is a crankshaft axis direction line 9, the straight line direction which is located on the bottom surface of the cylinder cover and is perpendicular to the crankshaft axis direction line 9 is a reference direction 8, the included angle between the flow guide protrusion characteristic line 6 and the reference direction 8 is a flow guide protrusion characteristic angle, and the flow guide protrusion characteristic angle is 60-120 degrees, and is further preferably designed to be 90 degrees. As shown in fig. 4, the first flow guide protrusion characteristic angle θ 1 and the second flow guide protrusion characteristic angle θ 2 corresponding to the two air inlet throats 10 are both 60 ° to 120 °. Due to the arrangement, the guide protrusions 5 can guide the inlet airflow to the direction far away from the adjacent inlet throats 10, so that the inlet airflow of the two adjacent inlet throats 10 is prevented from colliding, and high inlet energy is kept.

Preferably, the minimum distance h from the guide protrusion feature line 6 to the intake valve seat ring center line 3 (corresponding to the intake valve seat ring center 7 in fig. 3) is greater than 0 and equal to or less than 0.5 times the outer diameter d of the intake valve seat ring 1, and specifically, the minimum distance h may be 0.1 times, or 0.2 times, or 0.3 times, or 0.4 times, or 0.5 times the outer diameter d of the intake valve seat ring 1. So set up, not only can lead the air current of admitting air, but also can guarantee sufficient air flue flow coefficient.

Preferably, the angle theta 3 between the connecting line of the centers of two adjacent air inlet throats 10 (namely the connecting line 11 of the centers of the air inlet throats in the figure 5) and the axial direction line 9 of the crankshaft is 60-90 degrees. So configured, the branch air inlet corresponding to the two air inlet throats 10 forms a vertical air inlet structure, that is, the air inlet structure with the central connecting line 11 of the air inlet throats arranged perpendicular or nearly perpendicular to the axis direction line 9 of the crankshaft.

Preferably, the included angle theta 4 between the upper diversion inclined plane 14 and the upper end face of the intake valve seat ring 1 (namely the upper end face 17 of the intake valve seat ring in fig. 6) is 30-60 degrees, and the included angle theta 5 between the lower diversion inclined plane 15 and the lower end face of the intake valve seat ring 1 is 30-60 degrees.

Preferably, the radius R of the circular arc line 13 is greater than 0 and equal to or less than 0.2 times the outer diameter d of the intake valve seat ring 1, and specifically, the radius R of the circular arc line 13 may be 0.1 times or 0.2 times the outer diameter d of the intake valve seat ring 1. By such a design, the flow resistance can be further reduced.

Further preferably, as shown in fig. 6, a distance a between the center of the circular arc line 13 and the upper end surface 17 of the intake valve seat ring is greater than 0 and equal to or less than 0.2 times the outer diameter d of the intake valve seat ring 1, and specifically, the distance a may be 0.1 times or 0.2 times the outer diameter d of the intake valve seat ring 1. So set up, can guarantee that upper water conservancy diversion inclined plane 14 has sufficient guiding distance.

Preferably, as shown in fig. 2, the branch intake duct where each intake throat 10 is located is further provided with a tumble flow generating sharp angle 2, the tumble flow generating sharp angle 2 is located on one side wall surface of the branch intake duct away from the corresponding exhaust throat 12 and above the intake valve seat ring 1, and the tumble flow generating sharp angle 2 protrudes toward the intake valve seat ring center line 3 relative to the wall surface of the branch intake duct. When the intake air flow passes through the tumble generating sharp corner 2, most of the intake air flow is extruded to the opposite side, namely, is guided towards the direction close to the exhaust throat 12, therefore, the intake air flow moves towards the direction close to the exhaust throat 12 and far away from the adjacent intake throat 10 under the double diversion effects of the tumble generating sharp corner 2 and the diversion bulge 5 on the inner ring of the intake valve seat ring 1, and after the intake air flow moves to the lower area of the exhaust throat 12, the large-scale tumble motion is formed more easily under the further guiding effect of the cylinder wall and the piston. For the cylinder cover with two inlet throats 10, the inlet airflow of the two inlet throats 10 forms two large-scale tumble motions when entering the cylinder, and the cylinder cover has high inlet energy and stability.

Preferably, the axial projection of the tumble flow generating cusp 2 on the upper end surface 17 of the intake valve seat ring is a cusp projection 18, the cusp projection 18 is a convex region that protrudes from the inner edge of the intake valve seat ring 1 in the radial direction toward the center of the intake valve seat ring 1, and the width of the cusp projection 18 is greater in the middle in the circumferential direction of the intake valve seat ring 1 than in both ends thereof.

It should be noted that one side edge of the tumble flow generating sharp corner 2 facing the center 7 of the intake valve seat ring is a tumble flow sharp corner characteristic edge, the tumble flow sharp corner characteristic edge can be specifically designed to be a linear edge or a curved edge, and the formed sharp corner projection 18 has various shapes, preferably, in the present scheme, the tumble flow sharp corner characteristic edge is designed to be a curved edge, and the corresponding sharp corner projection 18 is a crescent-shaped area with a concave side facing the center 7 of the intake valve seat ring, as shown in fig. 7.

Preferably, as shown in fig. 2, the minimum distance L of the tumble flow generating tip angle 2 from the intake valve seat ring center line 3 is greater than 0 and equal to or less than 0.5 times the minimum diameter Dv of the sealing tapered surface 16 of the intake valve seat ring 1, and specifically, the minimum distance L may be 0.1 times or 0.2 times or 0.3 times or 0.4 times or 0.5 times the minimum diameter Dv of the sealing tapered surface 16.

The cylinder cover provided by the invention has the following beneficial effects:

1) on the basis of the traditional diesel engine cylinder cover, tumble motion with certain strength can be organized only by changing the structures of the air inlet channel and the air inlet valve seat ring 1, and meanwhile, part of vortex strength can be maintained, so that the method has higher feasibility and reduces the change cost;

2) according to the invention, the flow guide bulges 5 are designed on the inner wall of the inlet valve seat ring 1, and the arrangement structures of the adjacent flow guide bulges 5 are reasonably arranged, so that the proportion of the inlet airflow flowing out from the area between the two adjacent inlet throats 10 is reduced, the proportion of the airflow flowing out from the ring to other areas is increased, the airflow collision is avoided, and the energy loss is reduced;

3) the invention also designs the characteristic of a tumble generation sharp angle 5 in the branch air inlet channel, thereby further guiding the air flow to the exhaust side, being beneficial to generating large-scale tumble motion in the cylinder and being beneficial to improving the turbulent kinetic energy at the final stage of compression.

The invention also provides a gas engine comprising the cylinder cover. The derivation process of the beneficial effects generated by the gas engine is substantially similar to the derivation process of the beneficial effects brought by the cylinder cover, and therefore, the description is omitted.

The embodiments in the present description are described in a progressive manner, each embodiment focuses on differences from other embodiments, and the same and similar parts among the embodiments are referred to each other.

The previous description of the disclosed embodiments is provided to enable any person skilled in the art to make or use the present invention. Various modifications to these embodiments will be readily apparent to those skilled in the art, and the generic principles defined herein may be applied to other embodiments without departing from the spirit or scope of the invention. Thus, the present invention is not intended to be limited to the embodiments shown herein but is to be accorded the widest scope consistent with the principles and novel features disclosed herein.