CN214533265U - Cylinder head and gas engine - Google Patents

Cylinder head and gas engine Download PDF

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Publication number
CN214533265U
CN214533265U CN202121945222.2U CN202121945222U CN214533265U CN 214533265 U CN214533265 U CN 214533265U CN 202121945222 U CN202121945222 U CN 202121945222U CN 214533265 U CN214533265 U CN 214533265U
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flow
air inlet
cylinder head
throat
channel
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李卫
吕顺
李军银
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Weichai Power Co Ltd
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Weichai Power Co Ltd
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    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/12—Improving ICE efficiencies
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/30—Use of alternative fuels, e.g. biofuels

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Abstract

The utility model discloses a cylinder head and gas engine reforms transform the gas engine who forms on being applied to diesel engine's basis, including the intake duct that forms in the cylinder head, the intake duct includes public air channel and first branching runner, the second branching runner that forms at the terminal branching of public air channel, the effective volume V of first branching runner1Greater than the second forkEffective volume V of flow channel2(ii) a Initial end flow area S of first branch flow passage1Is larger than the initial end flow area S of the second branch flow passage2And S is1And S2Satisfies the relationship: s1=k（V1/V2）S2And k is an allowable preset deviation coefficient. By adopting the structure of the cylinder cover, the problem that the tumble effect is reduced due to the different flow at the positions of the two air inlet throats corresponding to the inlet valve seat rings is solved, and the tumble effect in the combustion chamber of the gas engine which is improved and developed on the basis of the diesel engine is also improved.

Description

Cylinder head and gas engine
Technical Field
The utility model relates to an engine technical field that admits air especially relates to a cylinder head and 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.
SUMMERY OF THE UTILITY MODEL
The utility model aims at providing a cylinder head and gas engine to improve the tumble flow effect in the gas engine's of development on promoting diesel engine's the basis.
In order to achieve the above object, the present invention provides a cylinder head, which is applied to a gas engine reformed based on a diesel engine, and comprises an air inlet channel formed on the cylinder head, wherein the air inlet channel comprises a common air channel and a first branch flow channel and a second branch flow channel which are formed by branching the tail end of the common air channel, and the common air channel is used for leading the air flow introduced from the air inlet of the cylinder head to the tail end of the common air channel in an even flow guiding manner; a first air inlet throat is formed at the tail end of the first branched flow passage, a second air inlet throat is formed at the tail end of the second branched flow passage, a first air inlet seat ring is arranged at the first air inlet throat, a second air inlet seat ring is arranged at the second air inlet throat, and the inner diameter of the first air inlet seat ring is equal to that of the second air inlet seat ring in diameter; effective volume V of the first diverging flow passage1Is larger than the effective volume V of the second branch flow passage2(ii) a A flow area S of an initial end of the first diverging flow passage1Is larger than the initial end flow area S of the second branched flow passage2And S is1And S2Satisfies the relationship: s1=k（V1/V2）S2And enabling the flow difference value of the outflow gas flow of the first air inlet throat and the outflow gas flow of the second air inlet throat to be within a preset deviation range, wherein k is an allowable preset deviation coefficient.
Preferably, the height of the start-end flow surface of the first diverging flow passage is the same as the height of the start-end flow surface of the second diverging flow passage, and the width D of the start-end flow surface of the first diverging flow passage1Is larger than the width D of the initial end flow surface of the second branched flow passage2。
Preferably, D is satisfied1＞D2On the premise of (D)1The value of (A) satisfies: d3≤D1≤3D3Wherein D is3Is the inner diameter of the first or second intake race.
Preferably, D is satisfied1＞D2On the premise of (D)2The value of (A) satisfies: 0 < D2≤1.5D3Wherein D is3Is the inner diameter of the first or second intake race.
Preferably, a center point of the end branch of the common gas flow passage is disposed at a distance H from an end face of the cylinder head where the gas inlet port is disposed, which satisfies: h is more than or equal to 0 and less than or equal to 3D3Wherein D is3Is the inner diameter of the first or second intake race.
Preferably, k is 0.8 to 1.1.
Preferably, the first branched air passage and the second branched air passage are both tumble guide air passages, and flow guide curved surface portions for guiding air to move towards the exhaust throat directions of the corresponding cylinder covers are arranged in the tumble guide air passages.
Preferably, the first branch air passage and the second branch air passage are both tumble guide air passages, the tumble guide air passages are obliquely arranged relative to the bottom surface of the cylinder head, one side wall surface of each tumble guide air passage close to the bottom surface of the cylinder head is a first wall surface, and the other side wall surface in each tumble guide air passage, which is opposite to the first wall surface, is a second wall surface; the flow guiding curved surface part is arranged on the first wall surface and/or the second wall surface.
Preferably, the diversion curved surface part is a fish-belly-shaped structure formed on the first wall surface and/or a fish-belly-shaped structure formed on the second wall surface.
Preferably, the flow guiding curved surface portion is a flow guiding protruding portion formed at the end edge of the first wall surface and respectively located above the first air inlet throat and the second air inlet throat, an axial projection of the flow guiding protruding portion on the upper end surface of each corresponding air inlet throat is a protruding projection, the protruding projection is located on the inner side of the corresponding air inlet throat and forms a protruding region protruding from the edge of the upper end surface of the air inlet throat towards the center of the air inlet throat along the radial direction, and the width of the middle portion of the protruding projection is greater than the width of the two ends of the protruding projection.
Preferably, the intake port is disposed at a side surface or a top surface or a bottom surface of the cylinder head.
Compared with the introduction content of the background technology, the cylinder cover is applied to the gas engine which is formed by transformation on the basis of the diesel engine, and comprises an air inlet channel formed on the cylinder cover, wherein the air inlet channel comprises a public air channel, a first branched channel and a second branched channel, the first branched channel and the second branched channel are branched at the tail end of the public air channel, and the public air channel is used for leading the air flow introduced from the air inlet of the cylinder cover to the tail end of the public air channel in a uniform flow guiding mode; a first air inlet throat is formed at the tail end of the first branched flow channel, a second air inlet throat is formed at the tail end of the second branched flow channel, a first air inlet seat ring is arranged at the first air inlet throat, a second air inlet seat ring is arranged at the second air inlet throat, and the inner diameter of the first air inlet seat ring is equal to that of the second air inlet seat ring; effective volume V of first branch flow passage1Is larger than the effective volume V of the second branch flow passage2(ii) a Initial end flow area S of first branch flow passage1Is larger than the initial end flow area S of the second branch flow passage2And S is1And S2Satisfies the relationship: s1=k（V1/V2）S2And enabling the flow difference value of the outflow gas flow of the first air inlet throat and the outflow gas flow of the second air inlet throat to be within a preset deviation range, wherein k is an allowable preset deviation coefficient. By adopting the structure of the cylinder cover, aiming at the air inlet channel, the tail end of the common air channel is branched to form the air channel structure of the first branched flow channel and the second branched flow channel, and the common air channel is led to the tail end of the common air channel in a uniform drainage mode, when the effective volume V of the first branched flow channel is1Is larger than the effective volume V of the second branch flow passage2In the case of (3), since the inner diameter of the first intake retainer is equal to the inner diameter of the second intake retainer, the flow area S at the start end of the first branch flow passage is set to be equal to the flow area S at the start end of the second branch flow passage1And the initial end flow area S of the second branch flow passage2Designed in an asymmetrical structure, i.e. with the initial flow area S of the first diverging flow passage1Is larger than the initial end flow area S of the second branch flow passage2And S is1And S2Satisfies the relationship: s1=k（V1/V2）S2Therefore, the flow difference value of the outflow gas flow of the first air inlet throat and the outflow gas flow of the second air inlet throat is in a preset deviation range, namely the density and the speed of the airflow entering the combustion chamber through the first air inlet throat and the second air inlet throat are basically consistent, the problem that the tumble effect is reduced due to the fact that the two air inlet throats correspond to different flow at the seat ring of the air inlet valve is solved, and the tumble effect in the combustion chamber of the developed gas engine is improved on the basis of the diesel engine is improved.
Additionally, the utility model also provides a gas engine, including the cylinder head, this cylinder head is the cylinder head that any scheme of the aforesaid described, because this cylinder head has above-mentioned technological effect, consequently the gas engine who has this cylinder head also should have corresponding technological effect, no longer gives unnecessary details here.
Drawings
Fig. 1 is a schematic structural diagram of an air inlet provided in an embodiment of the present invention;
fig. 2 is a schematic view of an inner diameter structure of the first/second inlet ring according to an embodiment of the present invention;
fig. 3 is a schematic structural view of a projected projection and a theoretical intake air flow port in a cylinder head structure provided in an embodiment of the present invention;
fig. 4 is a bottom view of the bottom surface of the cylinder head provided in the embodiment of the present invention.
In the above figures 1-4 of the drawings,
the air conditioner comprises a public air channel 1, a first air inlet throat 2, a second air inlet throat 3, a first branch flow channel 4, a second branch flow channel 5, a central point 6 of a tail end fork of the public air channel, a flow guide bulge part 7, a convex projection 71, a connecting line 72 of two ends, a convex direction line 73 and an exhaust throat center 8.
Detailed Description
The core of the utility model is to provide a cylinder head and gas engine to improve the tumble flow effect in the gas engine's of development on promoting diesel engine's the basis.
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 and fig. 2, an embodiment of the present invention provides a cylinder head, which is applied to a gas engine reformed on the basis of a diesel engine, and includes an air inlet formed in the cylinder head, the air inlet includes a common air channel 1, and a first branch channel 4 and a second branch channel 5 formed by branching at the end of the common air channel 1, the common air channel 1 is used for leading the air flow introduced from the air inlet of the cylinder head to the end of the common air channel 1 in an even flow guiding manner; a first air inlet throat 2 is formed at the tail end of the first bifurcated runner 4, a second air inlet throat 3 is formed at the tail end of the second bifurcated runner 5, a first air inlet seat ring is arranged at the first air inlet throat 2, a second air inlet seat ring is arranged at the second air inlet throat 3, and the inner diameter of the first air inlet seat ring is equal to that of the second air inlet seat ring in diameter; effective volume V of first branch flow channel 41Is larger than the effective volume V of the second branched runner 52(ii) a Initial end flow area S of first branch flow passage 41Is larger than the initial end flow area S of the second branched flow passage 52And S is1And S2Satisfies the relationship: s1=k（V1/V2）S2And enabling the flow difference value of the outflow gas flow of the first air inlet throat 2 and the outflow gas flow of the second air inlet throat 3 to be within a preset deviation range, wherein k is an allowable preset deviation coefficient.
By adopting the structure of the cylinder cover, when an engine cylinder inhales air, the inlet valve is opened, air flow flows into the public air flow channel from the air inlet on the outer side of the cylinder cover, the air channel structure of the first branched flow channel and the second branched flow channel is formed by branching the tail end of the public air flow channel aiming at the air inlet channel, and the public air flow channel leads to the tail end of the public air flow channel in an even drainage mode, when the first branched flow channel is used as the structure form of the first branched flow channelEffective volume V of1Is larger than the effective volume V of the second branch flow passage2In the case of (3), since the inner diameter of the first intake retainer is equal to the inner diameter of the second intake retainer, the flow area S at the start end of the first branch flow passage is set to be equal to the flow area S at the start end of the second branch flow passage1And the initial end flow area S of the second branch flow passage2Designed in an asymmetrical structure, i.e. with the initial flow area S of the first diverging flow passage1Is larger than the initial end flow area S of the second branch flow passage2And S is1And S2Satisfies the relationship: s1=k（V1/V2）S2Therefore, the flow difference value of the outflow gas flow of the first air inlet throat and the outflow gas flow of the second air inlet throat is in a preset deviation range, namely the density and the speed of the airflow entering the combustion chamber through the first air inlet throat and the second air inlet throat are basically consistent, the problem that the tumble effect is reduced due to the fact that the two air inlet throats correspond to different flow at the seat ring of the air inlet valve is solved, and the tumble effect in the combustion chamber of the developed gas engine is improved on the basis of the diesel engine is improved.
It should be noted that, as will be understood by those skilled in the art, the intake port is located outside the cylinder head. In addition, the allowable preset deviation coefficient k is a deviation coefficient caused by an allowable machining error, and generally satisfies S1Greater than S2On the basis of (1), the value can be selected to be 0.8-1.1.
In some embodiments, the initial flow area S of the first diverging flow passage1Is larger than the initial end flow area S of the second branch flow passage2In a specific embodiment, the height of the starting-end flow surface of the first branched flow path 4 may be the same as the height of the starting-end flow surface of the second branched flow path 5, and the width D of the starting-end flow surface of the first branched flow path 4 may be set to be equal to the width D of the starting-end flow surface of the second branched flow path 51Is larger than the width D of the initial end flow surface of the second branched flow passage 52. Since the first diverging flow passage and the second diverging flow passage are formed to be bifurcated at the end of the common flow passage, the arrangement space in the height direction of the flow cross section of the first/second diverging flow passage is limited and, in general, the height from the respective intake throats is the same, and therefore, by design, the first/second diverging flow passage has a limited height from the respective intake throatsWidth D of initial end flow surface of first branch flow passage 41Is larger than the width D of the initial end flow surface of the second branched flow passage 52In such a way that S is realized1And S2The corresponding relation between the two is more convenient to arrange.
In some specific embodiments, the design requirement of modifying the obtained gas engine on the basis of different diesel engines is met1＞D2On the premise of (D)1The value of (A) satisfies: d3≤D1≤1.5D3(ii) a Or D3≤D1≤2D3(ii) a Or D3≤D1≤2.5D3(ii) a Or D3≤D1≤3D3Wherein D is3Is the inner diameter of the first or second intake race. Also, when D is satisfied1＞D2On the premise of (D)2The value of (A) satisfies: 0 < D2≤0.5D3(ii) a Or 0 < D2≤0.8D3(ii) a Or 0 < D2≤1D3(ii) a Or 0 < D2≤1.5D3Wherein D is3Is the inner diameter of the first or second intake race.
In some more specific embodiments, the distance H of the center point 6 of the end branch of the common gas flow passage 1 from the end face of the cylinder head where the intake port is disposed may be specifically designed so as to satisfy: h is more than or equal to 0 and less than or equal to 0.5D3(ii) a Or H is more than or equal to 0 and less than or equal to 0.8D3(ii) a Or H is more than or equal to 0 and less than or equal to D3(ii) a Or H is more than or equal to 0 and less than or equal to 1.5D3(ii) a Or H is more than or equal to 0 and less than or equal to 2D3(ii) a Or H is more than or equal to 0 and less than or equal to 2.5D3(ii) a Or H is more than or equal to 0 and less than or equal to 3D3Wherein D is3Is the inner diameter of the first or second intake race.
In some specific embodiments, in order to make the air flow of the air inlet passage flowing into the combustion chamber have better tumble effect, generally speaking, a corresponding tumble guiding structure needs to be arranged in the air inlet passage. For example, the first branched flow passage 4 and the second branched flow passage 5 are both tumble guide flow passages, and a flow guide curved surface portion for guiding air to move towards the exhaust throat direction of the corresponding cylinder head is arranged in each tumble guide flow passage. The flow guide curved surface part can be a part or all of the wall surface of the first/second branched runner, and can also be designed into a pit curved surface or a convex curved surface which is positioned on the local part of the wall surface of the first/second branched runner, and when the air inlet air flow flows through the flow guide curved surface part, the flow guide curved surface part can generate guiding, throwing and other effects on the air flow.
Wherein, the basic principle when the tumble guiding structure works: when an engine cylinder inhales air, an inlet valve is opened, airflow enters a common airflow channel from an air inlet on the outer side of a cylinder cover, then flows into a first branched channel and a second branched channel respectively through tail end branched positions of the common airflow channel, and then enters the cylinder from a first/second air inlet throat respectively, the air inlet airflow moves towards the direction of an air outlet throat under the flow guide effect of each flow guide curved surface part, so that the airflow flowing to one side of the air outlet throat is enhanced, the airflow on one side of the air inlet throat is reduced, the airflow on two sides can more easily form large-scale tumble motion after entering the cylinder, further, the tumble intensity is enhanced, the turbulent flow can be favorably formed in the last stage of compression, and the heat efficiency of a gas engine is improved.
Therefore, on the basis of the existing diesel engine, the diversion curved surface part is designed through the first/second branched flow channel, so that the intake airflow generates the tumble effect required by the gas engine, and further the tumble strength and the heat efficiency of the gas engine are improved.
It should be noted that, in this scheme, the air inlet of the air inlet channel is opened on the outer side of the cylinder head, the other end of the air inlet channel is a first/second air inlet throat, and in the air inlet direction, the tumble guiding air channel is located at the downstream of the air inlet channel, wherein the tumble guiding air channel can be designed in various arrangement forms, such as inclined arrangement or vertical arrangement relative to the bottom surface of the cylinder head.
In some specific embodiments, when the tumble guide air passage is arranged obliquely with respect to the bottom surface of the cylinder head, one side wall surface of the tumble guide air passage that is close to the bottom surface of the cylinder head is a first wall surface, and the other side wall surface in the tumble guide air passage that is opposite to the first wall surface is a second wall surface; the flow guiding curved surface part is arranged on the first wall surface and/or the second wall surface.
The flow guide curved surface part can be specifically designed into an arc-shaped concave pit surface which is concave towards the bottom surface of the cylinder cover relative to the first wall surface, namely a fish-belly-shaped structure, and also can be designed into an arc-shaped concave pit surface which is concave towards the bottom surface of the cylinder cover relative to the second wall surface, and in the practical application process, the flow guide curved surface part can be selectively arranged according to the practical requirement.
In a further embodiment, the flow guiding curved surface portion may also be a flow guiding protrusion 7 formed at the end edge of the first wall surface and respectively located above the first air inlet throat 2 and the second air inlet throat 3, an axial projection of the flow guiding protrusion 7 on the upper end surface of each corresponding air inlet throat is a protrusion projection, the protrusion projection is located inside the corresponding air inlet throat and forms a protrusion area protruding from the edge of the upper end surface of the air inlet throat toward the center of the air inlet throat along the radial direction, and the width of the middle portion of the protrusion projection is greater than the widths of the two ends thereof, as shown in fig. 3. Specifically, when being provided with a plurality of water conservancy diversion curved surface portions on the first wall, the upside border of water conservancy diversion bulge meets with the downside border of last water conservancy diversion curved surface portion, and the downside border of water conservancy diversion bulge meets with the upside border of the inlet throat mouth that corresponds. Certainly, only the flow guide curved surface part formed by the flow guide protruding part can be arranged on the first wall surface, and the flow guide curved surface part can be arranged according to specific requirements in the practical application process. In this scheme, after the air current that admits air flows through last water conservancy diversion curved surface portion, this water conservancy diversion curved surface portion casts the air current to the second wall of offside, the water conservancy diversion bulge in this water conservancy diversion curved surface portion low reaches further makes the air current to the extrusion of second wall direction to the air current of the exhaust throat direction that has strengthened the flow direction and corresponds has reduced the air current that this intake throat kept away from exhaust throat one side, this both sides air current forms stronger tumble motion after getting into in the cylinder, thereby satisfy gas engine's combustion demand.
It should be noted that the flow guiding protrusion 7 in this embodiment is used to extrude a part of the air flow toward the exhaust throat before the intake air flow is injected into the intake throat, and the flow guiding protrusion 7 capable of implementing the above function may be designed in various structural shapes, for example, one side edge of the flow guiding protrusion 7 facing the center of the intake throat is designed to be an arc shape, a straight shape, a broken line shape or other curved structures. Preferably, the convex projection in this solution is a crescent-shaped area, and the concave side of the crescent-shaped area is arranged toward the center of the air inlet throat, i.e. one side edge of the flow guiding protrusion 7 toward the center of the air inlet throat is designed into a concave arc shape.
It should be noted that the flow guide protrusion 7 specifically includes an upper flow guide surface and a lower processing surface, the juncture of the upper flow guide surface and the lower processing surface is the edge of the flow guide protrusion 7 protruding toward the center of the air inlet throat, the lower processing surface is the processing surface formed after partial material of the cylinder head main body is removed by the flow guide protrusion processing characteristics, the flow guide protrusion processing characteristics specifically can adopt casting processing, rotary cutting processing and the like, and according to different structures of the flow guide protrusion 7, the lower processing surface specifically can be designed as a rotary processing surface, or a plurality of planes connected in sequence, or other curved surface structures and the like. Preferably, the lower side processing surface in the scheme is a rotary processing surface surrounding a processing axis, the processing axis can be designed to be coincident with, parallel to or obliquely arranged relative to the axis of the air inlet throat, and a generatrix of the rotary processing surface is a straight line, a broken line or a curve. The rotary processing surface removes partial material of the cylinder head body to form the flow guide bulge 7.
It should be noted that, according to different bus 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 axis of the air intake throat, and the vertex of the conical processing surface is located above the air intake throat. The concrete shape of the flow guide protruding part 7 depends on the size of the conical angle of the conical processing surface, and the larger the conical angle is, the sharper the flow guide protruding part 7 is. Preferably, the value range of the cone angle of the conical processing surface in the scheme is 60-160 degrees, and in the range, the guide protrusion part 7 can be ensured to have a sharp enough angle, so that the flow velocity mutation and the extrusion effect on the air inlet flow are further enhanced.
The maximum flow port formed by the rotary machined surface in the upper end circular surface of the intake throat is a theoretical intake flow port, that is, the axial projection of the circular profile formed by the conical bottom of the rotary machined surface after the material of the cylinder head body is removed in the upper end circular surface of the intake throat forms the theoretical intake flow portAnd (4) a mouth. When the processing axis of the rotary processing surface is coincident with or parallel to the axis of the air inlet throat, the theoretical air inlet flow port is a circular flow port; when the processing axis of the rotary processing surface and the axis of the air inlet throat are arranged in a relatively inclined mode, the theoretical air inlet flow port is an oval flow port. The theoretical equivalent diameter of the air inlet flow port is DmThe inner diameter of the inlet valve seat ring (the minimum diameter of the inlet valve seat ring and the inlet valve sealing conical surface) is D3In this scheme, DmAnd D3The relationship between them satisfies: dm = 0.85 D3~ D3D ismD designed to be 85% -100%3In the process, the circulation capacity and the tumble effect can be in balanced fit, namely, the obvious tumble effect can be achieved under the condition of ensuring the minimum influence on the circulation capacity.
Referring to FIG. 3, the theoretical total area of the intake air flow ports is SaThe area of the projected projection 71 is SbSince the flow guide projection 7 does not allow part of the air flow to pass through, the area of the opening of the lower end of the tumble guide air passage for the actual circulating air flow (i.e., the actual intake air flow port area S shown by the hatched portion in fig. 3)c) Equal to the total area S of the theoretical inlet flow portaMinus the area S of the projected projection 71bI.e. Sa、Sb、ScThe relationship of the three satisfies: sa = Sb +Sc。
Area S of the projected projection 71aThe larger the airflow blocking effect of the guide protrusion 7 is, the more remarkable the degree of squeezing the airflow is, that is, the more remarkable the air velocity is increased, the greater the tumble strength is generated. In order to balance the tumble effect and the air passage circulation capacity, the area S of the projection 71 is projected in the schemebDesigned as the area S of the theoretical inlet flow porta15% to 50%, i.e., SaAnd SbSatisfies the following conditions: sb/Sa=0.15~0.5。
Preferably, a connecting line between a midpoint of a connecting line 72 (a connecting line between two end points P1 and P2, as shown in fig. 3) of two ends of the projection 71 and the center of the air inlet throat is a projection direction line 73, an included angle between a connecting line between the center of the air inlet throat and the center of the exhaust throat corresponding thereto and the projection direction line 73 is a projection direction angle β, as shown in fig. 4, the range of the projection direction angle β in the scheme is 0 ° to 45 °, and by such arrangement, the projecting side edge of the flow guide projection 7 can be arranged toward the adjacent exhaust throat, so that the large-scale tumble motion is controlled to fill the whole cylinder as much as possible. Wherein, the connecting line of the center of the air inlet throat and the center of the exhaust throat corresponding to the air inlet throat refers to the connecting line of the center of the air inlet throat and the center 8 of the exhaust throat, as shown in fig. 4.
Preferably, the convex projection 71 spans an arc angle θ of 90 ° -220 ° in the upper end face of the inlet throat. This feature defines the extent of the span of the flow directing projection 7 in the cross-section of the tumble flow directing air passage.
In a further embodiment, the air inlet can be specifically arranged on the side surface or the top surface or the bottom surface of the cylinder cover, and in the actual application process, the air inlet can be selectively arranged according to actual requirements, so that the installation arrangement of engines of different models is realized.
Additionally, the utility model also provides a gas engine, including the cylinder head, this cylinder head is the cylinder head that any scheme of the aforesaid described, because this cylinder head has above-mentioned technological effect, consequently the gas engine who has this cylinder head also should have corresponding technological effect, no longer gives unnecessary details here.
It is right above that the utility model provides a cylinder head and gas engine have carried out detailed introduction. 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 have been explained herein using specific examples, and the above descriptions of the embodiments are only used to help understand the core concepts of the present invention. It should be noted that, for those skilled in the art, without departing from the principle of the present invention, the present invention can be further modified and modified, and such modifications and modifications also fall within the protection scope of the appended claims.

Claims (12)

1. A cylinder cover is applied to a gas engine reformed on the basis of a diesel engine, and comprises an air inlet channel formed on the cylinder cover, and is characterized in that the air inlet channel comprises a public air channel (1), a first branch channel (4) and a second branch channel (5) which are branched at the tail end of the public air channel (1), and the public air channel (1) is used for leading air flow led in from an air inlet of the cylinder cover to the tail end of the public air channel (1) in a uniform flow guiding manner; a first air inlet throat (2) is formed at the tail end of the first branched flow channel (4), a second air inlet throat (3) is formed at the tail end of the second branched flow channel (5), a first air inlet seat ring is arranged at the first air inlet throat (2), a second air inlet seat ring is arranged at the second air inlet throat (3), and the inner diameter of the first air inlet seat ring is equal to the inner diameter of the second air inlet seat ring; effective volume V of the first branch flow passage (4)1Is larger than the effective volume V of the second branched flow passage (5)2(ii) a A flow area S of the first branch flow passage (4) at the start end1Is larger than the initial end flow area S of the second branched flow passage (5)2And S is1And S2Satisfies the relationship: s1=k（V1/V2）S2And enabling the flow difference value of the outflow gas flow of the first air inlet throat (2) and the outflow gas flow of the second air inlet throat (3) to be within a preset deviation range, wherein k is an allowable preset deviation coefficient.
2. The cylinder head according to claim 1, wherein the height of the start-end flow surface of the first branch flow passage (4) is the same as the height of the start-end flow surface of the second branch flow passage (5), and the width D of the start-end flow surface of the first branch flow passage (4)1Is larger than the width D of the initial end flow surface of the second branched flow passage (5)2。
3. The cylinder head of claim 2, wherein D is satisfied1＞D2On the premise of (D)1The value of (A) satisfies: d3≤D1≤3D3Wherein D is3Is the inner diameter of the first or second intake race.
4. The cylinder head of claim 2, wherein D is satisfied1＞D2On the premise of (D)2The value of (A) satisfies: 0 < D2≤1.5D3Wherein D is3Is the inner diameter of the first or second intake race.
5. A cylinder head according to claim 1, characterized in that the distance H of the center point (6) of the end branch of the common gas flow channel (1) from the end face of the cylinder head where the gas inlet is arranged is such that: h is more than or equal to 0 and less than or equal to 3D3Wherein D is3Is the inner diameter of the first or second intake race.
6. The cylinder head of claim 1, wherein k is 0.8 to 1.1.
7. The cylinder head according to claim 1, wherein the first diverging flow passage (4) and the second diverging flow passage (5) are both tumble guide flow passages having flow guide curved portions provided therein for guiding the flow of air in the direction of the exhaust throat of the respective cylinder head.
8. The cylinder head according to claim 7, wherein the tumble guide gas passage is arranged obliquely with respect to the bottom surface of the cylinder head, one side wall surface of the tumble guide gas passage that is close to the bottom surface of the cylinder head is a first wall surface, and the other side wall surface in the tumble guide gas passage that is opposite to the first wall surface is a second wall surface; the flow guiding curved surface part is arranged on the first wall surface and/or the second wall surface.
9. The cylinder head of claim 8, wherein the flow guide curved surface portion is a fish-bellied structure formed on the first wall surface and/or a fish-bellied structure formed on the second wall surface.
10. The cylinder head according to claim 8, wherein the flow guide curved surface portion is a flow guide protrusion (7) formed at a distal end edge of the first wall surface and respectively located above the first intake throat (2) and the second intake throat (3), an axial projection of the flow guide protrusion (7) on an upper end surface of each corresponding intake throat is a protrusion projection (71) located inside the corresponding intake throat and forming a protrusion area protruding from an edge of the upper end surface of the intake throat toward a center of the intake throat in a radial direction, and a width of a middle portion of the protrusion projection is larger than widths of both ends thereof.
11. The cylinder head of claim 1, wherein said intake port is disposed in a side or top or bottom surface of said cylinder head.
12. A gas engine comprising a cylinder head, characterized in that the cylinder head is a cylinder head according to any one of claims 1-11.
CN202121945222.2U 2021-08-19 2021-08-19 Cylinder head and gas engine Active CN214533265U (en)

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