CN104033233A - Combustion Chamber Structure Of Internal-combustion Engine - Google Patents
Combustion Chamber Structure Of Internal-combustion Engine Download PDFInfo
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- CN104033233A CN104033233A CN201410049096.0A CN201410049096A CN104033233A CN 104033233 A CN104033233 A CN 104033233A CN 201410049096 A CN201410049096 A CN 201410049096A CN 104033233 A CN104033233 A CN 104033233A
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- squish
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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
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- Combustion Methods Of Internal-Combustion Engines (AREA)
- Cylinder Crankcases Of Internal Combustion Engines (AREA)
Abstract
A combustion chamber structure of an internal-combustion engine is provided. A combustion chamber comprises a main combustion chamber and a gas-squeezing area. A gas inlet valve end, a gas discharging valve end and a sparking plug installation end are respectively disposed at the three sides of the internal surface of the main combustion chamber. The gas-squeezing area is disposed at an opposite side of the sparking plug. The gas-squeezing area and the sparking plug sandwiches a plane. The plane comprises two axes which are the gas inlet vale axis and the gas discharging valve axis. An obtuse-angle-shaped gas-squeezing edge on the gas-squeezing area is arranged to extrude towards the inside of a cylinder.
Description
Mutually quoting of related application
The present invention is directed to the Japanese patent application No.2013-047041 submitting on March 8th, 2013 and propose priority request, at the full content of first to file, be incorporated by reference herein.
Technical field
The present invention relates to the engine on a kind of vehicle that is arranged on motorcycle etc. for example, relate to a kind of chamber structure of internal-combustion engine.
Background technique
In this engine, the routine techniques of use is that suction port in firing chamber or the periphery of relief opening arrange squish region (squish area).Squish region is set and there is following effect: be present in the final stage of fresh air in the air-fuel mixture of outer part of the firing chamber compression stroke in four stroke cycle process and promoted by the center towards firing chamber.Squish as above region is set up, thereby has following effect: eddy current is created in air-fuel mixture more consumingly, and the speed of the travel of flame in combustion stroke increases, and shorten period of combustion, thereby prevents the increase of high combustion gas temperature.As mentioned above, the advantage of squish is, for example, finally improves combustion efficiency etc.
[patent documentation 1] Japanese patent gazette No.3842938
[patent document 2] Japanese laid-open patent communique No.2000-145462
Yet the squish gas shape according to conventional, has following problem: it is resultful improving in the output of the engine speed of high load area, but compare and there is standard shape and do not have the improvement effect of situation combustion efficiency of squish very little at low load area.
Especially, by experiment show, gone out: under lean burn condition, no matter at which engine rotary area, comparison with standard shape is not improved the region of specific fuel consumption in conventional squish shape yet, and lean burn condition is the effective means of low fuel consumption.
As disclosed in patent documentation 1, patent documentation 2 etc., known a kind of chamber structure about squish, this chamber structure can improve combustion efficiency.
Summary of the invention
Consider above-mentioned actual conditions, the object of the present invention is to provide the chamber structure of internal-combustion engine, it can improve combustion efficiency and output characteristics within the scope of larger engine speed.
A chamber structure for internal-combustion engine, comprising: recess, and this recess is arranged on the cylinder head inwall in the face of the upper surface of piston; Firing chamber, this firing chamber consists of main combustion chamber and squish region, and this main combustion chamber is formed by this recess; With suction valve port, outlet valve port and spark plug, port is installed, this suction valve port, this outlet valve port and this spark plug are installed three sides that port is arranged in the internal surface of this main combustion chamber; Wherein, this squish region is arranged on the opposite side of spark plug, and this crush-zone and this spark plug are clamping plane, and this plane comprises suction valve axis and these two axis of outlet valve axis; And the squish edge with obtuse angle shape on this squish region is set to interior side-prominent towards cylinder.
In addition, according in the chamber structure of internal-combustion engine of the present invention, the roughly neutral position of this squish edge placement in this squish region between this suction valve port and this outlet valve port.
In addition, according in the chamber structure of internal-combustion engine of the present invention, this squish region comprises territory, air inlet lateral areas and exhaust side region, and this territory, air inlet lateral areas and this exhaust side area configurations are corresponding with this suction valve port and this outlet valve port and are positioned at the both sides at this squish edge; And by this obtuse angle that the peripheral edge separately in this territory, air inlet lateral areas and this exhaust side region forms be shaped as converge on this squish edge top, obtuse angle near the hurried increase of its inclination.
In addition, according in the chamber structure of internal-combustion engine of the present invention, this squish edge in this squish region is connected to the sunk surface of this main combustion chamber by joint, this joint is towards the inside linear tilt of cylinder central axis, connecting surface is formed on the both sides of this joint, and each in this connecting surface all forms by having a plurality of curvature.
In addition, according in the chamber structure of internal-combustion engine of the present invention, along the line stretcher of this joint at this squish edge, be arranged to compare with the electrode of this spark plug more and lean on to suction valve lateral deviation.
In addition, according in the chamber structure of internal-combustion engine of the present invention, the second squish region is arranged on this spark plug side, and the squish edge of obtuse angle shape is arranged on the territory, air inlet lateral areas in this second squish region.
Accompanying drawing explanation
Figure 1A is the peripheral upper surface view according to the cylinder head of embodiment's engine.
Figure 1B is the peripheral side view according to the exhaust port of embodiment's engine.
Fig. 1 C is according to the left side view of the engine of the present embodiment.
Fig. 1 D is according to the peripheral side view of the air inlet port of the engine of the present embodiment.
Fig. 2 A is the sectional view along Figure 1A center line I-I.
Fig. 2 B is the sectional view along Figure 1A center line II-II.
Fig. 3 is according to the peripheral stereogram of the firing chamber of the cylinder head of the engine of the present embodiment.
Fig. 4 A is that explanation is according to the view of the structure example of the firing chamber of the engine of the present embodiment.
Fig. 4 B is that explanation is according to the view of the function of the firing chamber of the engine of the present embodiment.
Fig. 5 is the sectional view along Fig. 4 B center line III-III.
Embodiment
Hereinafter, with reference to accompanying drawing, illustrate according to the most preferred embodiment of the chamber structure of internal-combustion engine of the present invention.
According to the chamber structure of internal-combustion engine of the present invention, be typically applied to be arranged on the engine on the vehicle of motorcycle etc. for example, but its applicable object is not limited to this.In the present embodiment, applicable object is for example, the air-cooled four stroke cycle single-cylinder engine 10 shown in Figure 1A to Fig. 1 D as an example.Hereinafter, the explanation of the graphical representation of surfaces in space of assembly will suitably be saved as required.First, the unitary construction of the engine 10 of this example is described.For example, cylinder 11, cylinder head 12 and front cylinder head 13 are attached to crankcase continuously, and this crankcase rotatably supports and holds this crankshaft, and this crankshaft is flatly arranged on left and right directions.Air inlet port 14 and exhaust port 15 are arranged in cylinder head 12, and the gas handling system that air-fuel mixture is supplied to engine 10 is connected with air inlet port 14, and the vent systems that waste gas is discharged from engine 10 is connected with exhaust port 15.
In gas handling system, throttle valve body is arranged in the centre of gas-entered passageway, and this gas-entered passageway is formed between air cleaner and cylinder head 12, not signal in this layout plan.Throttle valve is maintained in throttle valve body, and throttle valve opening/closing is formed on the gas-entered passageway of throttle valve body inside.Throttle valve body is connected to air inlet port 14 via suction tude.Sparger is attached to suction tude, and fuel is sprayed from sparger and is provided to the air inlet being fed to from suction tude, thereby air-fuel mixture is provided to engine 10.
In addition, in vent systems, outlet pipe is attached to exhaust port 15.The combustion gas that are created in engine 10 pass through outlet pipes from exhaust port 15, and finally as waste gas, from baffler, discharge.
Further illustrate engine 10.Fig. 2 A is through spark plug 16 and along the sectional view of cylinder axis or central axis Z direction, and Fig. 2 B is through outlet valve axis and suction valve axis and along the sectional view of cylinder axis Z direction.Cylinder sleeve 17 is inserted in cylinder 11, and piston 18 is contained in cylinder sleeve 17 so that can to-and-fro motion.The crank pin rotor of crankshaft is supported in the crankcase of meaning not shown in the figures rotatably and the wrist pin 19 of piston 18 is coupled to each other via connecting rod.Piston 18 to-and-fro motion in cylinder axis Z direction, thereby crankshaft rotation.In addition,, in cylinder head 12, valve drive or valve system that cam, camshaft etc. form are included in cam shell 20.Cam chain chamber 21 is arranged near the of cylinder chamber and roughly along the direction parallel with cylinder axis Z, and cam chain turns round in cam chain chamber 21.This cam chain is wound and is placed between sprocket wheel (sprocket) and drive sprocket (drive sprocket), thereby valve drive is synchronously running along with the rotation of crankshaft, this sprocket wheel is attached to one end of the camshaft of valve drive, and this drive sprocket is attached to crankshaft.
Firing chamber 22 is formed on the bottom of cylinder head 12, and in the space of the upper surface of the piston 18 of upper dead center, air inlet port 14 and exhaust port 15 are communicated with firing chamber 22 respectively.Between firing chamber 22 and air inlet port 14, by suction valve 23, open and close, between firing chamber 22 and exhaust port 15, by outlet valve 24, open and close.These suction valves 23 and outlet valve 24 are driven and are controlled by valve drive.
Camshaft 25 is rotatably supported in cam shell 20 to be sandwiched between the valve rod 23a of suction valve 23 and the valve rod 24a of outlet valve 24.In addition, in this example, camshaft 25 extends upward at the Vertical Square of the paper of Fig. 2 B, and intake cam and exhaust cam are integrally formed in, it is axially upper and between it, have a predetermined interval.Each rocking arm bridge joint is between the valve rod 23a of these cams and suction valve 23 and the valve rod 24a of outlet valve 24.Each rocking arm is supported on pitman arm shaft 26 swingably, the two Vertical Square at the paper of Fig. 2 B of 27(extends upward) on.
Rocking arm under each above-mentioned state is resisted against on the top of valve rod 23a and valve rod 24a via the tappet being attached on its each point.Valve spring is attached at respectively the valve rod 23a of suction valve 23 and the valve rod 24a of outlet valve 24 around, and valve rod 23a or valve rod 24a are because the elastic force of valve spring is promoted towards valve closing direction conventionally.The elastic force that valve rod 23a and the valve rod 24a rotation by camshaft 25 overcomes valve spring via rocking arm is pressed and moves down, simultaneously using crankshaft as driving source.Thereby suction valve 23 and outlet valve 24 were opened in the scheduled time, that is, each air inlet port 14 or exhaust port 15 are communicated with firing chamber 22.
According in the chamber structure of internal-combustion engine of the present invention, firing chamber 22 consists of recess 28, and recess 28 is formed in the inwall of cylinder head 12 as shown in Figure 3 and mainly in the face of the upper surface of piston 18.Recess 28 is approximate dome state, and forms the main combustion chamber of firing chamber 22.The present invention also comprises squish region 29, that is, firing chamber consists of main combustion chamber and squish region 29, and main combustion chamber consists of recess 28.In addition, suction valve port 30, outlet valve port 31 and spark plug are installed port 32 and are arranged in three sides,, in this example, on three positions of the internal surface of the main combustion chamber being formed by recess 28, form T-shaped shape, suction valve 23 is attached to suction valve port 30, and outlet valve 24 is attached to outlet valve port 31, and spark plug 16 is attached to spark plug port 32 is installed.Especially, spark plug 16 is correspondingly arranged on the underpart of T-shaped shape, that is, it is arranged to close to the peripheral of firing chamber 22 rather than at dome-type center.
In the present embodiment, as shown in Figure 3, squish region 29 is arranged on the opposite side of spark plug 16, is clamping planar S between it, and this planar S is become by the axis X of suction valve 23 and the axis Y shape of outlet valve 24.
In the present invention, particularly, in squish region 29 as shown in Figure 4 A, the squish edge 33 with obtuse angle shape (its obtuse angle is θ) arranges highlightedly towards the inner side of cylinder.
Squish region 29 is the M shape shape as shown in Fig. 4 A etc., and squish edge 33 is correspondingly positioned at the center of M shape shape.In this case, squish edge 33 is arranged to the roughly position of centre corresponding to suction valve port 30 and outlet valve port 31.
In addition, squish region 29 comprises air inlet lateral areas territory 29A and exhaust side region 29B, and air inlet lateral areas territory 29A and exhaust side region 29B are positioned at the both sides at squish edge 33, corresponding to suction valve port 30 and outlet valve port 31 as shown in Figure 4 A.The obtuse angle shape at squish edge 33 (obtuse angle θ) is with reference to figure 4B by each the peripheral edge 29a(of inner side of cylinder chamber that is positioned at air inlet lateral areas territory 29A and exhaust side region 29B) form.Each peripheral edge 29a is in the crooked bent state that caves in towards the outside of cylinder chamber, when radius of curvature R diminishes during towards squish edge 33 side, that is, keeps a plurality of radius of curvature R.Namely, near the top, obtuse angle of peripheral edge 29a convergence, the hurried increase of inclination α of the obtuse angle shape at squish edge 33.In other words, all in all squish edge 33 is just obtuse angle, but each peripheral edge 29a of air inlet lateral areas territory 29A and exhaust side region 29B is relative, to rise gradually each other, by the relative formed angle of peripheral edge 29a, diminished, as the most advanced and sophisticated side at squish edge 33.
In addition, the squish edge 33 in squish region 29 is connected to sunk surface 28a with edge line state via joint 34, and this sunk surface 28a forms main combustion chamber (with reference to the oblique line part in figure 4A).The connecting surface 35(35A representing by oblique line in Fig. 4 B, 35B) be formed on the both sides of joint 34, and squish region 29 is connected via these connecting surfaces 35 with sunk surface 28a.In this case, connecting surface 35A, 35B have recessed curved surface, but its cross section in the Vertical direction of cylinder axis Z is the same with above-mentioned peripheral edge 29a, a plurality of radius of curvature, consist of.
In addition, the edge line of joint 34 slopes inwardly linearly towards cylinder axis Z on the vertical section parallel with cylinder axis Z.As shown in Figure 5, the squish edge 33 in squish region 29 is connected via joint 34 with sunk surface 28a, but joint 34 is straight line shapies, and tilts with angle beta with respect to cylinder axis Z inner side.In addition, the cross section of connecting surface 35A, 35B is identical with joint 34 is also straight line shape.
In addition, as shown in Figure 4 A, along the line stretcher T of the joint 34 at squish edge 33 than the electrode 16a of spark plug 16 more towards suction valve 23 lateral deviations from.Symbol in Fig. 4 A " t " is the deviant between joint 34 and spark plug 16 electrode 16a.
In addition as shown in Fig. 4 A, 4B, 36(the second squish region, another squish region) be arranged on spark plug 16 sides and squish edge 37Shi obtuse angle shape and be arranged on the air inlet lateral areas territory 36A in squish region 36.
In thering is the chamber structure of said structure, first, squish edge 33Shi obtuse angle shape and be arranged on the squish region 29 in firing chamber 22.Even if air-fuel mixture passes through by the little lower ventilated port of pressure drop (down draft port) or a little less than the disorder of the air inlet port 14 that directly port (straight port) etc. forms and mixture, by being arranged on the squish edge 33 between air inlet port 14 and exhaust port 15, generation is by deflect flow and peel off the eddy current causing, it is as air-fuel mixture F1 as shown in Figure 4 B, therefore, aggravated the disorder of air-fuel mixture.Notice because conventional squish shape is the curve shape that eases up stably and close, so air-fuel mixture peel off be difficult to occur in conventional squish shape and its disorder less.That is, in the present invention, can improve low load burning and not damage charge flow rate coefficient by effectively producing eddy current.
As mentioned above, the opposite side of spark plug 16 is arranged to roughly be positioned in squish edge 33, therefore has following effect: the not air-fuel mixture of combustion that is arranged in the region away from spark plug 16 of firing chamber 22 is pushed the disorder simultaneously increasing towards flame surface direction.Namely, by squish region 29 and squish edge 33, the mobile raising of air-fuel mixture and burning are flowed and are increased, so the burning in firing chamber 22 is accelerated.Especially, in the double cylinder engine with suction valve 23 and 24 two valves of outlet valve of the present embodiment, spark plug 16 can not be arranged in to 22 center, firing chamber, therefore the distance of the end from ignition point to firing chamber is inhomogeneous.In these cases, by improving the mobile of air-fuel mixture and burning to flow, can obtain higher burning acceleration effect.
In addition, squish edge 33 is arranged in the roughly position of centre between suction valve port 30 and outlet valve port 31.In this case, particularly in the obtuse angle at squish edge 33 shape peripheral edge 29a convergence, near the hurried increase of inclined angle alpha top, obtuse angle.The position at squish edge 33, shape etc. are set as mentioned above, so air-fuel mixture process air inlet port 14, and flow along so-called longitudinal wall surface, and this longitudinal wall surface is formed by the connecting surface 35A of air inlet lateral areas territory 29A especially.Near the squish edge 33 of M shape shape, the hurried increase of inclination α, therefore air-fuel mixture F2 is as shown in Figure 4 B stronger towards the directivity of the direction of spark plug 16.Thereby, can be fed to towards spark plug 16 directions the mixing fresh air of high combustion.
In addition, intilted connecting surface 35 is connected to the sunk surface 28a as main combustion chamber from the peripheral edge 29a in squish region 29.By connecting surface 35 in firing chamber 22 on a large scale in may there is squish and flow, the disorder that produces air-fuel mixture due to edge effect meeting during this period, so exist burning on a large scale to improve effect between main combustion period.In conventional squish, only have in fact at TDC(upper dead center) near, could obtain by the raw effect of squish miscarriage.
In addition, squish edge 33 is near spark plug 16 cornerwise, and flame propagation and velocity of combustion that therefore the combination meeting of above-mentioned effect is accelerated in whole firing chamber 22 increase.Especially in this case because squish edge 33 deflection suction valve 23 sides, so the air-fuel mixture that points to spark plug 16 directions not can away from or deflection exhaust side and more being strengthened towards the directivity of spark plug 16.Therefore, there will be for example prevent from clashing into, burning that the output of the Zone Full of engine speed improves etc. improves effect.In addition, can effectively improve the combustion stability under the lean burn condition of low fuel consumption, therefore, fuel consumption is enhanced.In addition, can guarantee the extremely smooth combustion of low load rotary area of high capacity rotary area from engine speed, therefore, as making fuel consumption and the improved technology of output, this is a kind of effective means.
Therefore in addition, the second shape squish edge, 36He obtuse angle, squish region 37 is arranged on spark plug 16 sides, and for the burning of the air-fuel mixture of spark plug 16 sides, the burning that also can obtain similar above-mentioned situation improves effect.
As mentioned above, the present invention is described by various embodiments, but the present invention is not limited to these embodiments, can in category of the present invention, change.
For example, in the above-described embodiments, described the example of bivalve engine, this bivalve engine has suction valve 23 and outlet valve 24, yet the present invention is also applicable to be called as the engine respectively with two suction valves and two outlet valves of four valve engines.In this case, spark plug is arranged in the center of firing chamber, and squish edge is arranged on position in the middle of air inlet side and exhaust side and right on the diametric(al) of cylinder chamber, and such structure also can be used.
In addition, in the above-described embodiments, described the example for the engine of motorcycle, but the present invention also can be applicable to the vehicle of four-wheel wagon for example or so-called ATV etc. effectively.
According to the present invention, by the eddy current of peeling off generation of deflect flow and air-fuel mixture, by squish edge, produced, and the disorder of air-fuel mixture is accelerated.In firing chamber, eddy current for air-fuel mixture is produced effectively, therefore can suppress by the reducing of the inlet end mouth-shaped charge flow rate coefficient that for example high cylinder port (high tumble port) causes, and then improve low load burning and can not reduce the output of high load area.Namely, can improve the output within the scope of wide range speed of combustion efficiency and engine.
It should be noted that above-described embodiment is only to realize illustrative example of the present invention, technical scope of the present invention is not defined by these embodiments.That is, can realize the present invention with various forms, these do not depart from the spirit and scope of the invention.
Claims (6)
1. a chamber structure for internal-combustion engine, is characterized in that, comprises:
Recess, described recess is arranged on the cylinder head inwall in the face of the upper surface of piston;
Firing chamber, described firing chamber consists of main combustion chamber and squish region, and described main combustion chamber is formed by described recess; With
Suction valve port, outlet valve port and spark plug are installed port, and described suction valve port, described outlet valve port and described spark plug are installed three sides that port is arranged in the internal surface of described main combustion chamber;
Wherein, described squish region is arranged on the opposite side of spark plug, and described crush-zone and described spark plug are clamping plane, and described plane comprises suction valve axis and these two axis of outlet valve axis; And
The squish edge with obtuse angle shape on described squish region is set to interior side-prominent towards cylinder.
2. the chamber structure of internal-combustion engine as claimed in claim 1, is characterized in that,
The roughly neutral position of the described squish edge placement in described squish region between described suction valve port and described outlet valve port.
3. the chamber structure of internal-combustion engine as claimed in claim 1 or 2, is characterized in that,
Described squish region comprises territory, air inlet lateral areas and exhaust side region, and territory, described air inlet lateral areas and described exhaust side area configurations are corresponding with described suction valve port and described outlet valve port and are positioned at the both sides at described squish edge; And
The described obtuse angle being formed by the peripheral edge separately in territory, described air inlet lateral areas and described exhaust side region be shaped as converge on described squish edge top, obtuse angle near the hurried increase of its inclination.
4. the chamber structure of internal-combustion engine as claimed any one in claims 1 to 3, is characterized in that,
The described squish edge in described squish region is connected to the sunk surface of described main combustion chamber by joint, described joint is towards the inside linear tilt of cylinder central axis, connecting surface is formed on the both sides of described joint, and each in described connecting surface all forms by having a plurality of curvature.
5. the chamber structure of internal-combustion engine as claimed in claim 4, is characterized in that,
Along the line stretcher of the described joint at described squish edge, be arranged to compare with the electrode of described spark plug more and lean on to suction valve lateral deviation.
6. the chamber structure of the internal-combustion engine as described in any one in claim 1 to 5, is characterized in that,
The second squish region is arranged on described spark plug side, and the squish edge of obtuse angle shape is arranged on the territory, air inlet lateral areas in described the second squish region.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2013047041A JP6115197B2 (en) | 2013-03-08 | 2013-03-08 | Combustion chamber structure of internal combustion engine |
| JP2013-047041 | 2013-03-08 |
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| Publication Number | Publication Date |
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| CN104033233A true CN104033233A (en) | 2014-09-10 |
| CN104033233B CN104033233B (en) | 2016-09-07 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201410049096.0A Active CN104033233B (en) | 2013-03-08 | 2014-02-12 | The chamber structure of internal combustion engine |
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| Country | Link |
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| JP (1) | JP6115197B2 (en) |
| CN (1) | CN104033233B (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104879234A (en) * | 2015-05-22 | 2015-09-02 | 奇瑞汽车股份有限公司 | Engine piston |
| CN109563787A (en) * | 2016-08-09 | 2019-04-02 | 阿凯提兹动力公司 | For port edge shape of the improved ring-port interaction and flow area with continuous curvature |
| CN111365139A (en) * | 2018-12-25 | 2020-07-03 | 长城汽车股份有限公司 | Cylinder head and internal combustion engine |
| WO2022016403A1 (en) * | 2020-07-22 | 2022-01-27 | 宁波吉利罗佑发动机零部件有限公司 | Engine combustion system, gasoline engine for hybrid vehicle, and vehicle |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP6399552B2 (en) * | 2014-09-30 | 2018-10-03 | 本田技研工業株式会社 | Internal combustion engine |
| KR102108189B1 (en) | 2018-01-23 | 2020-05-08 | 한국과학기술연구원 | Vapor leakage prevention type hydrogen peroxide sterilization system |
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| US5582147A (en) * | 1994-04-25 | 1996-12-10 | Hyundai Motor Company | Combustion chamber for internal combustion engine having multiple valves |
| US20050051130A1 (en) * | 2001-11-14 | 2005-03-10 | Lampard Robert Douglas | Internal combustion engine with divided combustion chamber |
| CN202117715U (en) * | 2011-05-11 | 2012-01-18 | 陈刚 | Air-inlet and air-distribution device of engine and engine formed by same |
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| JPS58117315A (en) * | 1981-07-29 | 1983-07-12 | Toyota Motor Corp | Combustion chamber for internal-combustion engine |
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| JPS59105926A (en) * | 1982-12-08 | 1984-06-19 | Honda Motor Co Ltd | Three valve type internal-combustion engine |
| JPH086594B2 (en) * | 1989-01-24 | 1996-01-24 | 日産自動車株式会社 | Combustion chamber of internal combustion engine |
| JPH07150946A (en) * | 1993-12-02 | 1995-06-13 | Daihatsu Motor Co Ltd | Spark-ignition type internal combustion engine |
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| US5582147A (en) * | 1994-04-25 | 1996-12-10 | Hyundai Motor Company | Combustion chamber for internal combustion engine having multiple valves |
| US20050051130A1 (en) * | 2001-11-14 | 2005-03-10 | Lampard Robert Douglas | Internal combustion engine with divided combustion chamber |
| CN202117715U (en) * | 2011-05-11 | 2012-01-18 | 陈刚 | Air-inlet and air-distribution device of engine and engine formed by same |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104879234A (en) * | 2015-05-22 | 2015-09-02 | 奇瑞汽车股份有限公司 | Engine piston |
| CN104879234B (en) * | 2015-05-22 | 2019-01-01 | 奇瑞汽车股份有限公司 | A kind of engine piston |
| CN109563787A (en) * | 2016-08-09 | 2019-04-02 | 阿凯提兹动力公司 | For port edge shape of the improved ring-port interaction and flow area with continuous curvature |
| CN109563787B (en) * | 2016-08-09 | 2022-05-10 | 阿凯提兹动力公司 | Port edge shape with continuous curvature |
| CN111365139A (en) * | 2018-12-25 | 2020-07-03 | 长城汽车股份有限公司 | Cylinder head and internal combustion engine |
| WO2022016403A1 (en) * | 2020-07-22 | 2022-01-27 | 宁波吉利罗佑发动机零部件有限公司 | Engine combustion system, gasoline engine for hybrid vehicle, and vehicle |
Also Published As
| Publication number | Publication date |
|---|---|
| CN104033233B (en) | 2016-09-07 |
| JP2014173498A (en) | 2014-09-22 |
| JP6115197B2 (en) | 2017-04-19 |
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