CN114810327A - Combustion chamber and gas engine - Google Patents
Combustion chamber and gas engine Download PDFInfo
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- CN114810327A CN114810327A CN202210549852.0A CN202210549852A CN114810327A CN 114810327 A CN114810327 A CN 114810327A CN 202210549852 A CN202210549852 A CN 202210549852A CN 114810327 A CN114810327 A CN 114810327A
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- 238000002485 combustion reaction Methods 0.000 title claims abstract description 157
- 230000009286 beneficial effect Effects 0.000 abstract description 12
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- 102000001999 Transcription Factor Pit-1 Human genes 0.000 description 39
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- 239000007789 gas Substances 0.000 description 27
- 238000007906 compression Methods 0.000 description 8
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- 241001270131 Agaricus moelleri Species 0.000 description 7
- 230000006835 compression Effects 0.000 description 7
- 230000008859 change Effects 0.000 description 4
- 238000009795 derivation Methods 0.000 description 4
- 238000005266 casting Methods 0.000 description 2
- 238000011161 development Methods 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- VNWKTOKETHGBQD-UHFFFAOYSA-N methane Chemical compound C VNWKTOKETHGBQD-UHFFFAOYSA-N 0.000 description 2
- 238000002407 reforming Methods 0.000 description 2
- 238000004088 simulation Methods 0.000 description 2
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- 238000004364 calculation method Methods 0.000 description 1
- 238000006243 chemical reaction Methods 0.000 description 1
- 125000004122 cyclic group Chemical group 0.000 description 1
- 239000003344 environmental pollutant Substances 0.000 description 1
- 238000001125 extrusion Methods 0.000 description 1
- 239000000446 fuel Substances 0.000 description 1
- 230000006872 improvement Effects 0.000 description 1
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- 230000004048 modification Effects 0.000 description 1
- 239000003345 natural gas Substances 0.000 description 1
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B23/00—Other engines characterised by special shape or construction of combustion chambers to improve operation
- F02B23/08—Other engines characterised by special shape or construction of combustion chambers to improve operation with positive ignition
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
- F02F3/00—Pistons
- F02F3/26—Pistons having combustion chamber in piston head
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- Combustion & Propulsion (AREA)
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- General Engineering & Computer Science (AREA)
- Combustion Methods Of Internal-Combustion Engines (AREA)
Abstract
The invention discloses a combustion chamber and a gas engine, wherein the combustion chamber is used for the gas engine reformed by a diesel engine, the combustion chamber is combined with a weak tumble cylinder cover structure for use, the combustion chamber comprises a cylinder cover bottom surface and a combustion chamber pit positioned at the top of a piston, the surface of the combustion chamber pit is a rotary smooth curved surface, the cylinder cover bottom surface comprises a rotary arc-shaped cylinder cover pit positioned above the combustion chamber pit, and the central line of the combustion chamber pit is closer to an exhaust valve relative to the central line of the arc-shaped cylinder cover pit. The combustion chamber has a better streamline curved surface structure, is beneficial to the formation of tumble flow, and meanwhile, the combustion chamber concave pit and the arc cylinder cover concave pit are designed asymmetrically, so that the energy loss in the tumble flow process can be reduced, the turbulent kinetic energy in the combustion chamber is further enhanced, the flame propagation speed is increased, and the heat efficiency of an engine is improved.
Description
Technical Field
The invention relates to the technical field of engines, in particular to a combustion chamber and a gas engine.
Background
At present, the design and development of natural gas engines are generally improved on the basis of diesel engines, and for diesel engines, vortex generated by a cyclone air passage is beneficial to mixing of oil bundles and air to a certain extent, so that high-efficiency combustion and low pollutant emission are realized. The gas engine is premixed combustion, fuel is mixed with air in the air intake process, and after a spark plug is ignited to generate a fire core, the ideal state is that high turbulent kinetic energy exists in a cylinder in the combustion process. The increase of the turbulent kinetic energy can accelerate the flame propagation speed, which has great significance for improving the combustion process of the gas engine and reducing the cycle variation. If large-size flow such as vortex continues to exist in the gas engine, the flow velocity near the spark plug is low at the end of compression, the longitudinal flow velocity is also low, the vortex cannot be broken into small-size turbulence, so that the turbulent kinetic energy is low, and therefore, the large-size vortex motion is not beneficial to premixed combustion of the gas engine. For a gas engine, the turbulent kinetic energy can be improved by properly improving the tumble strength of the mixed gas, so that the combustion characteristic of the gas is improved. Wherein, the vortex is the organized large-scale rotational flow motion of the gas around the central axis of the cylinder; the tumble refers to large-scale rotational flow movement of airflow organized around an axis vertical to the central axis of the cylinder; in addition, turbulent flow is different from laminar flow, and refers to a small-scale rotational flow which is generated in many directions and is not fixed when the airflow speed is high.
Due to the middle air inlet mode and casting deviation of the diesel engine, the consistency of the swirl ratio is poor, and the consistency of each cylinder is poor. On the premise that a valve rod of a diesel engine cannot be inclined, a roof-type combustion chamber similar to a gasoline engine cannot be achieved, so that tumble strength is low, a straight piston is usually adopted by a gas engine to match with tumble, the combustion speed of the current gas engine is still low, the piston needs to be further optimized, the tumble degree is enhanced, the flame propagation speed is increased, and the heat efficiency of the engine is improved.
The existing cylinder cover of the gas engine generally adopts the cylinder cover of the diesel engine directly, and the bottom surface of the cylinder cover is flat, namely, a flat-top combustion chamber structure is adopted, so that the air flow in the cylinder is not beneficial to forming tumble flow. In addition, the existing gas engine piston is generally formed by reforming a diesel engine piston, a pit 01 of a combustion chamber of the piston is mostly in a straight-mouth structure, as shown in fig. 1, due to the existence of large-scale vortex motion, the flame development form is influenced, the cyclic variation is high, and the flame propagation speed and the improvement of the heat efficiency of the whole engine are limited.
Therefore, how to optimize the combustion chamber structure of the gas engine to improve the thermal efficiency of the engine is a technical problem to be solved by those skilled in the art.
Disclosure of Invention
In view of the above, the present invention is directed to a combustion chamber and a gas engine, and the present invention is advantageous to form tumble in a cylinder and increase turbulent kinetic energy by optimizing a structure of the combustion chamber and combining with an existing weak tumble air passage, so as to increase a flame propagation speed and improve a thermal efficiency of the engine.
In order to achieve the purpose, the invention provides the following technical scheme:
the utility model provides a combustion chamber for the gas engine who is reformed transform by the diesel engine, the combustion chamber uses with weak tumble inlet passage combination, the combustion chamber includes the cylinder head bottom surface and is located the combustion chamber pit at the top of piston, the surface of combustion chamber pit is the rounding off surface of gyration shape, the cylinder head bottom surface is including being located the arc cylinder head pit of the gyration shape of the top of combustion chamber pit, the central line of combustion chamber pit is relative the central line of arc cylinder head pit is closer to the exhaust valve.
Preferably, the surface of the arc-shaped cylinder cover pit and the surface of the combustion chamber pit are both spherical arc surfaces, and the curvature radius of the arc-shaped cylinder cover pit is larger than that of the combustion chamber pit.
Preferably, the deepest depression of the arc-shaped cylinder cover pit is 0-4 mm, and the depth of the combustion chamber pit is 0.2-0.5 times of the diameter of the piston.
Preferably, the radius of curvature of the combustion bowl is between 0.2 and 0.3 times the diameter of the piston.
Preferably, the diameter of the upper edge of the combustion pocket is 0.5 to 0.75 times the diameter of the piston.
Preferably, the diameter of the lower edge of the arc-shaped cylinder cover pit is larger than or equal to the diameter of the upper edge of the combustion chamber pit.
Preferably, the central line of the arc-shaped cylinder cover pit coincides with the central line of the piston, and the central line of the combustion chamber pit is arranged in parallel with the central line of the piston.
Preferably, the central connecting line direction of the combustion chamber pit and the arc-shaped cylinder cover pit is parallel to the central connecting line direction of the intake valve and the exhaust valve.
Preferably, the distance between the central line of the combustion chamber pit and the central line of the arc-shaped cylinder cover pit is 0-4 mm.
The combustion chamber provided by the invention is used for a gas engine reformed by a diesel engine, the combustion chamber is combined with a weak tumble inlet channel for use, the combustion chamber comprises a cylinder cover bottom surface and a combustion chamber pit positioned at the top of a piston, the surface of the combustion chamber pit is a rotary smooth curved surface, the cylinder cover bottom surface comprises a rotary arc-shaped cylinder cover pit positioned above the combustion chamber pit, and the center line of the combustion chamber pit is closer to an exhaust valve relative to the center line of the arc-shaped cylinder cover pit.
The working principle of the invention is as follows:
the invention designs the arc cylinder cover pit on the bottom surface of the cylinder cover, and designs the combustion chamber pit as the revolving round and smooth curved surface pit, thereby leading the combustion chamber to have a better streamline curved surface structure and being beneficial to the formation of tumble flow.
The invention also provides a gas engine comprising any one of the combustion chambers described above. The derivation process of the beneficial effect of the gas engine is substantially similar to the derivation process of the beneficial effect of the combustion chamber, 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 diagram of a prior art straight piston;
FIG. 2 is a cross-sectional view of a combustion chamber in an embodiment of the invention;
FIG. 3 is a graph of the dimensional relationship of an arcuate cylinder head pocket and a combustion chamber pocket in an exemplary embodiment of the present invention;
FIG. 4 is a schematic cross-sectional view of an embodiment of the present invention;
FIG. 5 is a schematic diagram of airflow when a prior art flat-top cylinder head operates at top dead center in conjunction with a straight-nose piston;
FIG. 6 is a schematic illustration of the airflow of the combustion chamber as the piston travels to TDC in an exemplary embodiment of the present invention;
FIG. 7 is a graph comparing the change in tumble ratio of the prior art and the present invention;
fig. 8 is a graph comparing the instantaneous heat release rate change of the prior art and the present invention.
The meaning of the various reference numerals in figures 1 to 8 is as follows:
01-combustion chamber pits;
the engine comprises a piston 1, a combustion chamber pit 2, a cylinder cover 3, an arc cylinder cover pit 4, a combustion chamber pit center line 5, an arc cylinder cover pit center line 6, a cylinder cover bottom 7, an intake valve 8, an exhaust valve 9, a straight-opening piston 10 and a flat-top cylinder cover 11.
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 8, the present invention provides a combustion chamber for a gas engine reformed from a diesel engine, and the combustion chamber is used in combination with a weak tumble inlet channel, so as to further improve tumble strength in a cylinder, wherein the weak tumble inlet channel refers to an inlet channel described in the patent of the invention ("a weak tumble rapid combustion system and a gas engine", publication No. CN111287860A "), specifically, an inlet channel of a cylinder head can enable an inlet airflow to generate a large-scale weak tumble motion in the cylinder, and specific weak tumble structure design features thereof are not described herein again. The cylinder cover structure corresponding to the combustion chamber is formed by reforming a flat-top diesel engine cylinder cover, the top surface (namely the bottom surface 7 of the cylinder cover) of the formed combustion chamber is not a plane structure any more, but an arc-shaped pit structure with a certain radian is designed on the bottom plane of the cylinder cover. Specifically, the combustion chamber comprises a bottom surface of a cylinder cover 3 and a combustion chamber pit 2 positioned on the top of a piston 1, the surface of the combustion chamber pit 2 is a round curved surface in a revolution shape, the cylinder cover bottom surface 7 comprises a curved cylinder cover pit 4 in a revolution shape positioned above the combustion chamber pit 2, and the center line of the combustion chamber pit 2 (shown as a combustion chamber pit center line 5 in fig. 2) is closer to an exhaust valve relative to the center line of the curved cylinder cover pit 4 (shown as a curved cylinder cover pit center line 6 in fig. 2). Wherein, the bottom of the combustion chamber pit 2 is also a smooth curved surface, so that the airflow entering the combustion chamber pit 2 can smoothly flow through the side wall of the pit and the surface of the bottom of the pit. The arc-shaped cylinder cover pit 4 can be formed by casting, or the arc-shaped cylinder cover pit 4 can be machined on the bottom surface of the flat-top cylinder cover in a machining mode, and the like.
The working principle of the invention is as follows:
during air inlet, most of inlet air flow is rushed to the area below the exhaust valve, so that the inlet air flow flows into the combustion chamber pit 2 from the side wall of the pit at the side of the exhaust valve, and then the inlet air flow further flows along the smooth surface of the combustion chamber pit 2. Meanwhile, the combustion chamber pit 2 and the arc cylinder cover pit 4 are designed asymmetrically, so that when the piston 1 reaches the position near the top dead center, tumble airflow in the combustion chamber pit 2 can directly enter the arc cylinder cover pit 4, and tumble airflow in the arc cylinder cover pit 4 can also directly enter the combustion chamber pit 2 of the piston 1, so that energy loss in a tumble process can be reduced, the tumble can be broken into more small-scale turbulence at the end of a compression stroke, turbulent energy in the combustion chamber is further enhanced, flame propagation speed is increased, and heat efficiency of an engine is improved.
It should be noted that the surface of the combustion chamber pit 2 may be a smooth curved surface such as a spherical arc surface or an ellipsoidal arc surface, and the surface of the arc-shaped cylinder cover pit 4 may also be a smooth curved surface such as a spherical arc surface or an ellipsoidal arc surface, in short, the surfaces of the combustion chamber pit 2 and the arc-shaped cylinder cover pit 4 in the present invention are both revolution curved surfaces and have a smooth transition curved surface structure in the cylinder tumble flow direction. In a preferred embodiment, the surface of the arc-shaped cylinder cover pit 4 and the surface of the combustion chamber pit 2 are both spherical arc surfaces, and the curvature radius of the arc-shaped cylinder cover pit 4 is greater than that of the combustion chamber pit 2, specifically, as shown in fig. 2, a plane passing through the central line 5 of the combustion chamber pit and parallel to the central line direction of the intake and exhaust valves is a combustion chamber longitudinal symmetric surface, an intersection line of the arc-shaped cylinder cover pit 4 and the combustion chamber longitudinal symmetric surface is an arc-shaped cylinder cover pit molded line, an intersection line of the combustion chamber pit 2 and the combustion chamber longitudinal symmetric surface is a combustion chamber pit molded line, the arc-shaped cylinder cover pit molded line and the combustion chamber pit molded line are both arc lines, the radius of the combustion chamber pit molded line is significantly less than that of the arc-shaped cylinder cover pit molded line, and the combustion chamber pit 2 forms a pit structure similar to a hemisphere in whole.
Preferably, the deepest recess of the arc-shaped cylinder head pocket 4 (depth H1 as shown in fig. 3) is 0 to 4mm, and the depth H2 of the combustion chamber pocket 2 is 0.2 to 0.5 times the piston diameter D1, that is, H2 is (0.2 to 0.5) D1.
Preferably, as shown in fig. 3, the radius of curvature R1 of the combustion bowl 2 is 0.2 to 0.3 times the piston diameter D1, i.e., R1 is (0.2 to 0.3) D1. Since the combustion chamber pit 2 and the arc-shaped cylinder head pit 4 are both of a curved surface structure of revolution, the upper edge of the combustion chamber pit 2 forms one circular edge, and further preferably, the diameter D2 of the upper edge of the combustion chamber pit 2 is 0.5 to 0.75 times the piston diameter D1, that is, D2 is (0.5 to 0.75) D1. So set up, can guarantee that piston 1 satisfies the compression ratio requirement, make combustion chamber pit 2 have the space of sufficient tissue tumble simultaneously.
In a preferred embodiment scheme, the diameter of the lower edge of the arc cylinder cover pit 4 is more than or equal to the diameter of the upper edge of the combustion chamber pit 2, so the arrangement is that gas entering the cylinder through the air inlet channel can flow to the upper edge of the combustion chamber pit 2 on the exhaust valve side along the surface of the arc cylinder cover pit 4 firstly, then flows downwards along the wall surface of the combustion chamber pit 2 and flows towards the direction of the air inlet valve, and the airflow flowing upwards from the bottom of the combustion chamber pit 2 can smoothly enter the arc cylinder cover pit 4 above, so that the tumble strength is enhanced.
It should be noted that the arc-shaped cylinder cover pit center line 6 may be designed to coincide with, intersect with, or be parallel to the piston center line, and the combustion chamber pit center line 5 may also be designed to coincide with, intersect with, or be parallel to the piston center line, and in a preferred embodiment, in order to facilitate processing of the cylinder cover 3 and the piston 1, the arc-shaped cylinder cover pit center line 6 in this embodiment coincides with the piston center line, and the combustion chamber pit center line 5 is arranged parallel to the piston center line.
It should be noted that, the central line 5 of the combustion chamber pit is closer to the exhaust valve side than the central line 6 of the arc cylinder cover pit, so the edge position of the combustion chamber pit 2 is closer to the exhaust valve side than the edge position of the arc cylinder cover pit 4, wherein, preferably, the central connecting line direction of the combustion chamber pit 2 and the arc cylinder cover pit 4 is parallel to the central connecting line direction of the intake valve and the exhaust valve, so the arrangement can make the guiding airflow direction of the combustion chamber pit 2 consistent with the rolling direction of the intake direction, thereby being beneficial to further improving the tumble strength in the cylinder.
Further preferably, the distance Δ d between the center line 5 of the combustion chamber pit and the center line 6 of the arc-shaped cylinder cover pit is 0-4 mm, as shown in fig. 3.
Preferably, the junction between the upper edge of the combustion chamber pit 2 and the upper top surface of the piston is a transition fillet. By the design, the resistance of airflow flowing between the arc-shaped cylinder cover pit 4 and the combustion chamber pit 2 can be further reduced, and high energy is kept.
The air intake process and the compression process of the present invention will be described in detail with reference to fig. 4 to 6:
fig. 5 to 6 show a cross-section of the combustion chamber in the position of section a-a as shown in fig. 4, and it can be seen that the engine cylinder to which it is applied is provided with two inlet valves 8 and two exhaust valves 9, respectively, and the two open arrows in fig. 4 represent the general intake direction and the general exhaust direction, respectively. As shown in fig. 5, during the intake process, the straight-mouth type piston 10 in the prior art runs upwards along the hollow arrow direction in fig. 5, when the straight-mouth type piston 10 reaches the vicinity of the top dead center, because the cylinder cover corresponding to the combustion chamber is the flat-top type cylinder cover 11 and is matched with the straight-mouth type piston 10, the combustion chamber is compressed into a space similar to a cylinder, and the space is not beneficial to the formation of tumble flow, so that the tumble strength is low. Meanwhile, because the flow extrusion intensity of the air inlet and the air outlet is consistent, the turbulent kinetic energy of the air flow in the spark plug area in the center of the combustion chamber is low, which is not beneficial to the rapid propagation of flame.
As shown in FIG. 6, the partial bottom surface 7 of the cylinder cover is designed into an arc-shaped pit structure, and the combustion chamber pit 2 with a spherical arc surface is matched, so that the combustion chamber has a better streamline curved surface structure, and therefore, when the piston 1 runs to the position near the top dead center, the formation of tumble flow and the enhancement of tumble flow strength are facilitated. In addition, because arc cylinder cap pit 4 and combustion chamber pit 2 adopt asymmetric design for the tumble air current in the combustion chamber pit 2 can directly enter into arc cylinder cap pit 4, the tumble air current in the arc cylinder cap pit 4 also can directly enter into combustion chamber pit 2, thereby can reduce the energy loss of tumble in-process, the tumble can be broken into more small-scale torrents at compression stroke's final stage, and then the turbulent kinetic energy in the reinforcing combustion chamber, improve flame propagation speed, the thermal efficiency of promotion engine.
Referring to fig. 7 and 8, fig. 7 is a graph comparing the change of tumble ratio between the prior art and the present invention;
fig. 8 is a graph comparing the instantaneous heat release rate change of the prior art and the present invention.
The common working condition area is selected as a calculation working condition, the tumble ratio and the instantaneous heat release rate of an original scheme (a scheme of a straight-mouth type piston and a flat-top type cylinder cover structure) and the scheme (a scheme of a hemispherical pit and an arc pit cylinder cover structure) are compared by utilizing three-dimensional simulation calculation software, the comparison result is shown in fig. 7 and 8, according to the simulation result, at an ignition moment (a crank angle of-21 degrees), the tumble ratio of the scheme is obviously higher than that of the original scheme, the heat release rate is advanced, and the heat release is accelerated. Specifically, as shown in fig. 7, compared with the original scheme, in the middle and later stages of the intake stroke and the compression stroke, the tumble flow of the scheme is strengthened, and in the later stage of the compression stroke, the tumble flow is broken, the tumble ratio is sharply reduced, and the tumble ratio corresponding to the original scheme tends to be consistent. As shown in fig. 8, the exhaust temperature of the original scheme under the low-load working condition is too low, so that the post-treatment conversion efficiency is too low; compared with the original scheme, the scheme has the advantages that the combustion speed in the early stage is obviously improved, the combustion speed in the later stage is slower, the low-load exhaust temperature is favorably maintained, and meanwhile, the generation amount of NOx is also reduced.
In summary, there are three large scale flow patterns for gas flow within a gas engine cylinder: tumble, vortex and squeeze flow, three flow modes mutually influence in the air inlet organization and the combustion process, and influence the combustion process to different degrees. The invention designs a combustion chamber structure with an arc pit cylinder cover matched with a hemispherical piston pit, and has three core ideas: 1) under the condition that a weak tumble air passage is not changed, the scheme enhances the tumble strength in the cylinder to accelerate combustion, particularly, the bottom surface of the cylinder cover 3 is changed from an original plane structure into an arc-shaped shallow concave pit structure, so that the formation of airflow tumble in the cylinder is facilitated, and the turbulent kinetic energy of the piston when the piston runs to the position near a top dead center is increased; 2) the piston pit is changed from a traditional straight port type into a smooth curved surface, and is preferably designed into a hemispherical pit structure, so that the air flow entering the pit is organized to form tumble flow in the processes of air inlet and compression, and the tumble flow strength is further enhanced; 3) this scheme adopts asymmetric design with arc cylinder cap pit 4 and combustion chamber pit 2, and the combustion chamber pit 2 of piston 1 is to exhaust valve one side skew certain distance, and the tumble air current in the guide combustion chamber pit 2 enters into the arc cylinder cap pit 4 of 3 bottoms of cylinder head, simultaneously, also can make the tumble air current in the arc cylinder cap pit 4 enter into the piston pit 2 of below, and then strengthen holistic tumble flow intensity.
The invention also provides a gas engine comprising any one of the combustion chambers described above. The derivation process of the beneficial effect of the gas engine is substantially similar to the derivation process of the beneficial effect of the combustion chamber, and therefore, the description is omitted.
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.
Claims (10)
1. The utility model provides a combustion chamber for the gas engine who reforms by the diesel engine, the combustion chamber uses with weak tumble inlet passage combination, a serial communication port, the combustion chamber includes the cylinder head bottom surface and is located the combustion chamber pit at the top of piston, the surface of combustion chamber pit is the rounding off surface of gyration shape, the cylinder head bottom surface is including being located the arc cylinder head pit of the gyration shape of the top of combustion chamber pit, the central line of combustion chamber pit is relative the central line of arc cylinder head pit is more close to the exhaust valve.
2. The combustion chamber of claim 1 wherein the surface of the curved head pocket and the surface of the combustion chamber pocket are both spherically curved surfaces and the radius of curvature of the curved head pocket is greater than the radius of curvature of the combustion chamber pocket.
3. The combustion chamber as claimed in claim 2, wherein the deepest recess of the arc-shaped cylinder cover pit is 0-4 mm, and the depth of the combustion chamber pit is 0.2-0.5 times the diameter of the piston.
4. The combustion chamber of claim 2 wherein said combustion pocket has a radius of curvature of between 0.2 and 0.3 times said piston diameter.
5. The combustion chamber of claim 4 wherein the upper edge of said combustion pocket has a diameter between 0.5 and 0.75 times the diameter of said piston.
6. The combustion chamber of claim 5 wherein a diameter of a lower edge of the curved head pocket is equal to or greater than a diameter of an upper edge of the combustion chamber pocket.
7. The combustion chamber of any of claims 2-6 wherein a centerline of the curved cylinder head pocket coincides with a piston centerline, the centerline of the combustion chamber pocket being arranged parallel to the piston centerline.
8. The combustion chamber as claimed in claim 7, wherein the direction of the connecting line of the centers of the combustion chamber pit and the arc-shaped cylinder cover pit is parallel to the direction of the connecting line of the centers of the intake valve and the exhaust valve.
9. The combustion chamber of claim 7, wherein a distance between a centerline of the combustion chamber pocket and a centerline of the curved cylinder head pocket is 0-4 mm.
10. A gas engine characterized by comprising a combustion chamber according to any one of claims 1 to 9.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202210549852.0A CN114810327A (en) | 2022-05-20 | 2022-05-20 | Combustion chamber and gas engine |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202210549852.0A CN114810327A (en) | 2022-05-20 | 2022-05-20 | Combustion chamber and gas engine |
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| CN114810327A true CN114810327A (en) | 2022-07-29 |
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| CN202210549852.0A Withdrawn CN114810327A (en) | 2022-05-20 | 2022-05-20 | Combustion chamber and gas engine |
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Citations (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5335635A (en) * | 1992-07-22 | 1994-08-09 | Fuji Jukogyo Kabushiki Kaisha | Combustion chamber for an internal combustion engine |
| US5813385A (en) * | 1996-10-08 | 1998-09-29 | Fuji Jukogyo Kabushiki Kaisha | Combustion chamber structure having piston cavity |
| CN2773327Y (en) * | 2004-05-31 | 2006-04-19 | 胡济荣 | Piston of IC engine |
| CN109236486A (en) * | 2018-11-02 | 2019-01-18 | 滨州渤海活塞有限公司 | Internal combustion engine novel steel pistons and internal combustion engine |
| CN110608089A (en) * | 2018-06-15 | 2019-12-24 | 丰田自动车株式会社 | Internal combustion engine |
| US20200123999A1 (en) * | 2017-04-04 | 2020-04-23 | Nissan Motor Co., Ltd. | Piston |
| CN111287860A (en) * | 2020-05-13 | 2020-06-16 | 潍柴动力股份有限公司 | Weak tumble fast combustion system and gas engine |
| CN111486019A (en) * | 2020-06-28 | 2020-08-04 | 潍柴动力股份有限公司 | Combustion chamber and gas engine |
| CN214221354U (en) * | 2020-11-25 | 2021-09-17 | 重庆隆鑫通航发动机制造有限公司 | Engine combustion chamber |
| CN113482765A (en) * | 2021-08-11 | 2021-10-08 | 安徽江淮汽车集团股份有限公司 | Natural gas engine |
| CN113738498A (en) * | 2021-09-02 | 2021-12-03 | 潍柴动力股份有限公司 | Combustion system and gas engine with same |
-
2022
- 2022-05-20 CN CN202210549852.0A patent/CN114810327A/en not_active Withdrawn
Patent Citations (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5335635A (en) * | 1992-07-22 | 1994-08-09 | Fuji Jukogyo Kabushiki Kaisha | Combustion chamber for an internal combustion engine |
| US5813385A (en) * | 1996-10-08 | 1998-09-29 | Fuji Jukogyo Kabushiki Kaisha | Combustion chamber structure having piston cavity |
| CN2773327Y (en) * | 2004-05-31 | 2006-04-19 | 胡济荣 | Piston of IC engine |
| US20200123999A1 (en) * | 2017-04-04 | 2020-04-23 | Nissan Motor Co., Ltd. | Piston |
| CN110608089A (en) * | 2018-06-15 | 2019-12-24 | 丰田自动车株式会社 | Internal combustion engine |
| CN109236486A (en) * | 2018-11-02 | 2019-01-18 | 滨州渤海活塞有限公司 | Internal combustion engine novel steel pistons and internal combustion engine |
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| CN113482765A (en) * | 2021-08-11 | 2021-10-08 | 安徽江淮汽车集团股份有限公司 | Natural gas engine |
| CN113738498A (en) * | 2021-09-02 | 2021-12-03 | 潍柴动力股份有限公司 | Combustion system and gas engine with same |
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