CN104879233A - Direct-injection type diesel engine - Google Patents
Direct-injection type diesel engine Download PDFInfo
- Publication number
- CN104879233A CN104879233A CN201510307298.5A CN201510307298A CN104879233A CN 104879233 A CN104879233 A CN 104879233A CN 201510307298 A CN201510307298 A CN 201510307298A CN 104879233 A CN104879233 A CN 104879233A
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- CN
- China
- Prior art keywords
- piston
- diesel engine
- diameter
- direct injection
- cylinder head
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
- 238000002347 injection Methods 0.000 title claims abstract description 27
- 239000007924 injection Substances 0.000 title claims abstract description 27
- 239000003921 oil Substances 0.000 claims abstract description 23
- 239000000295 fuel oil Substances 0.000 claims abstract description 11
- 230000015572 biosynthetic process Effects 0.000 claims description 3
- 238000010304 firing Methods 0.000 description 11
- 238000000034 method Methods 0.000 description 11
- 238000002485 combustion reaction Methods 0.000 description 7
- 238000004519 manufacturing process Methods 0.000 description 7
- 239000000446 fuel Substances 0.000 description 6
- 238000001816 cooling Methods 0.000 description 5
- 229910052799 carbon Inorganic materials 0.000 description 4
- OKTJSMMVPCPJKN-UHFFFAOYSA-N Carbon Chemical compound [C] OKTJSMMVPCPJKN-UHFFFAOYSA-N 0.000 description 3
- 239000002245 particle Substances 0.000 description 3
- 239000004071 soot Substances 0.000 description 3
- 239000000470 constituent Substances 0.000 description 2
- 239000000203 mixture Substances 0.000 description 2
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 2
- 241001416181 Axis axis Species 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000033228 biological regulation Effects 0.000 description 1
- -1 carbon hydrogen compound Chemical class 0.000 description 1
- 238000005266 casting Methods 0.000 description 1
- 238000006243 chemical reaction Methods 0.000 description 1
- 239000000110 cooling liquid Substances 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 239000002283 diesel fuel Substances 0.000 description 1
- 230000007613 environmental effect Effects 0.000 description 1
- 239000003344 environmental pollutant Substances 0.000 description 1
- 229910052739 hydrogen Inorganic materials 0.000 description 1
- 239000001257 hydrogen Substances 0.000 description 1
- 239000002184 metal Substances 0.000 description 1
- 231100000719 pollutant Toxicity 0.000 description 1
- 238000012958 reprocessing Methods 0.000 description 1
- 239000007921 spray Substances 0.000 description 1
- 239000002912 waste gas Substances 0.000 description 1
Classifications
-
- 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
- F02F1/00—Cylinders; Cylinder heads
- F02F1/24—Cylinder heads
- F02F1/42—Shape or arrangement of intake or exhaust channels in cylinder heads
- F02F1/4285—Shape or arrangement of intake or exhaust channels in cylinder heads of both intake and exhaust channel
-
- 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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
- F02M61/14—Arrangements of injectors with respect to engines; Mounting of injectors
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Combustion Methods Of Internal-Combustion Engines (AREA)
Abstract
The invention discloses a direct-injection type diesel engine which comprises a plurality of air cylinders and cylinder covers. A mixed groove is arranged in the top of a piston in each air cylinder, each mixed groove comprises a radial flange, a lower groove body and an upper groove body, the side wall of the lower groove body comprises a big-end-down cone part and an arc part from top to bottom, the cone part extends downwardly from the radial flange, a boss is arranged at the position of the bottom center of the lower groove, the top surface of the boss is identical to the lower end of the cone part in height, and the arc part is clamped between the bottom of the boss and the lower end of the cone part; the diameter of the upper groove body increases from the radial flange to the top surface of the piston gradually; oil injectors corresponding to the air cylinders are arranged on the cylinder covers, axes of the cylinder covers are coincided with the central axis of the piston, and fuel oil injected out from multiple oil injection holes of the oil injectors are injected to the lower groove body; two air inlet ports and one exhaust port are arranged at the positions, corresponding to the air cylinders in the cylinder covers. Compared with a two-valve diesel engine, inflating efficiency of the air cylinders is improved, and engine performance and exhaust level are improved.
Description
Technical field
The present invention relates to engine art, particularly a kind of diesel engine with direct injection.
Background technique
Existing diesel engine with direct injection usually adopt each working cylinder to arrange structure that two valves (i.e. an intake valve and an exhaust valve) or each working cylinder arrange Four valve (i.e. two intake valves and two exhaust valves).
The charging efficiency of the diesel engine with direct injection of two valves is poor, and the oil sprayer of diesel engine relative to cylinder and piston axis bias and tilt, therefore the firing chamber in piston top must be biased to make it roughly be positioned at the below of oil sprayer, firing chamber is more responsive for cylinder head swirl rate parameter, the rotary motion of the fuel/air mixture simultaneously in firing chamber is uneven relative to cylinder axis axis and length from the jet path of the fuel of spray-hole different in oil sprayer is normally different, this causes air not good with mixing of fuel oil, performance and the emission level of diesel engine are poor.
The piston combustion bowl of Four valve diesel engine with direct injection oil sprayer and cylinder holes coaxial positioning, and the shape of firing chamber is had nothing in common with each other.But the form parameter of in fact a lot of firing chamber is undesirable, the mixing of air and fuel is caused not reach the best, fuel cannot perfect combustion, combustion efficiency low, the emission level of pollutant is undesirable, in firing chamber, carbon soot particles level is very high, therefore carbon soot particles can only be filled into by the reprocessing of cost intensive the level that environmental regulation requires to atmospheric discharge amount, significantly improves cost of production.Further, the casting technique of the cylinder head of four-valve diesel engine is complicated, and position, ridge area cooling difficulty, affects the thermal fatigue life (especially for the diesel engine with direct injection of little cylinder diameter) of cylinder head.
The information being disclosed in this background technique part is only intended to increase the understanding to general background of the present invention, and should not be regarded as admitting or imply in any form that this information structure has been prior art that persons skilled in the art are known.
Summary of the invention
The object of the present invention is to provide a kind of diesel engine with direct injection, thus overcome the air of two valve diesel and fuel oil mixing is not good, and four-valve diesel engine cannot the low defect of the thermal fatigue life of perfect combustion and cylinder head.
For achieving the above object, the invention provides a kind of diesel engine with direct injection, diesel engine with direct injection comprises: multiple cylinder, piston is provided with in each cylinder, the top of piston is provided with the mixing groove of the axisymmetrical about piston, the cross section of mixing groove is in " ω " shape, and mixing groove comprises: radial flange, and radial flange is arranged on the middle and upper part of the inwall of mixing groove; Lower recess, lower recess is positioned at the below of radial flange, the sidewall of lower recess from top to bottom comprises up-small and down-big tapered portion and arc portion, tapered portion from radial flange to downward-extension, the place of bottom centre of lower recess is provided with boss, boss is frusto-conical, and the end face of boss and the lower end of tapered portion are in same horizontal plane, and arc portion is folded between the bottom of boss and the lower end of tapered portion; And upper grooves, upper grooves is positioned at the top of radial flange, and the diameter of upper flange increases to the end face of piston gradually from radial flange; And cylinder head, cylinder head is provided with the oil sprayer corresponding with each cylinder, the axis of oil sprayer and the central axes of piston, the uniform multiple nozzle opening in end of oil sprayer, and the fuel oil of multiple nozzle opening ejection is injected in lower recess; Position corresponding with each cylinder in cylinder head is provided with two air inlet ports and an exhaust port.
Preferably, in technique scheme, the three-dimensional cone angle that the injection direction of multiple nozzle opening ejection is formed is obtuse angle.
Preferably, in technique scheme, the maximum diameter of upper grooves is 0.61 ~ 0.71 times of the diameter of piston, and the diameter of radial flange is 0.5 ~ 0.6 times of the diameter of piston, and the maximum diameter of lower recess is 0.56 ~ 0.60 times of the diameter of piston.
Preferably, in technique scheme, the maximum depth of mixing groove is 0.15 ~ 0.18 times of the diameter of piston, upper grooves the degree of depth be 0.02 ~ 0.05 times of the diameter of piston, the distance of the top of boss and the end face of piston is 0.05 ~ 0.09 times of the diameter of piston.
Preferably, in technique scheme, the angle of boss is 110 ° ~ 130 °.
Preferably, in technique scheme, the formation ridge area, region between adjacent air inlet port and between adjacent air inlet port and exhaust port, the width of ridge area is not less than 7mm.
Preferably, in technique scheme, cylinder head is single camshaft cylinder head.
Preferably, in technique scheme, cylinder head is twin cam shaft cylinder head.
Preferably, in technique scheme, cylinder head surface is smooth to the surface of piston.
Compared with prior art, the present invention has following beneficial effect:
Relative to two valve diesel, invention increases the charging efficiency of cylinder, the geomery parameter simultaneously by mixing groove comes Optimizing Combustion room, thus improves the burning of diesel engine, effectively improves engine performance and emission level; Three valve be arranged on the internal structure simplifying cylinder head water cavity to a certain extent, guarantee that there are enough layout cooling channels, space the maximum valve ridge area of heat load, decrease manufacture difficulty and manufacture cost while reducing cost of production, and decrease the component of some.
Accompanying drawing explanation
Fig. 1 is the sectional view of cylinder according to diesel engine with direct injection of the present invention and cylinder head.
Fig. 2 is the Local map of the bottom surface according to cylinder head of the present invention.
Fig. 3 is the sectional drawing according to piston of the present invention.
Main Reference Numerals illustrates:
1-cylinder head, 2-oil sprayer, 3-cylinder wall, 4-piston, 5-mixing groove, 6-firing chamber, 7-cylinder head bottom surface, 8-air inlet port, 9-exhaust port, 10-central axis, 11-ridge area, 12-oil sprayer port, 13-boss, 14-upper grooves, 15-lower recess, 16-radial flange.
Embodiment
Below in conjunction with accompanying drawing, the specific embodiment of the present invention is described in detail, but is to be understood that protection scope of the present invention not by the restriction of embodiment.
Clearly represent unless otherwise other, otherwise in whole specification and claims, term " comprise " or its conversion as " comprising " or " including " etc. by be understood to include the element of stating or constituent element, and do not get rid of other element or other constituent element.
As shown in Figure 1, comprise cylinder head 1 and multiple cylinder according to the diesel engine with direct injection of the specific embodiment of the invention, in each cylinder, be provided with piston 4, piston 4 to-and-fro motion in cylinder.The firing chamber of each cylinder is formed by the top of inside with the cylinder wall 3 of cooling jacket, cylinder head bottom surface 7 and piston 4.
As shown in figs. 1 and 3, the top of piston 4 is provided with the mixing groove 5 of the axisymmetrical about piston 4.The middle and upper part of the inwall of mixing groove is provided with radial flange 16, and the diameter of radial flange 16 is the minimum diameter of mixing groove 5.Mixing groove 5 is separated into upper grooves 14 and lower recess 15 by radial flange 16.
The sidewall of lower recess 15 from top to bottom comprises up-small and down-big tapered portion and arc portion, tapered portion from radial flange 16 to downward-extension.The center of the bottom of lower recess 15 is provided with boss 13, and boss 13 is in frusto-conical, and the end face of boss 13 and the lower end of tapered portion are in same horizontal plane.Between the bottom that arc portion is folded in boss 13 and the lower end of tapered portion.The diameter of upper grooves 14 increases gradually from the end face of radial flange 16 to piston 4, there is certain distance between the top edge of upper grooves 14 and the external cylindrical surface of piston 4.
Preferably, as shown in Figure 3, the diameter of setting piston 4 is D, and the maximum dimension D 1 of upper grooves 14 is 0.61D ~ 0.71D, and lower recess 15 maximum dimension D 2 is 0.56 ~ 0.60D, and the diameter D3 of radial flange 16 is 0.5D ~ 0.6D.The angle α of boss 13 is 110 ° ~ 130 °.The depth H 1 of upper grooves 14 is 0.02D ~ 0.05D.Boss 13 is 0.05D ~ 0.09D with the distance H2 of the end face of piston 4.The maximum depth H3 of mixing groove 5 is 0.15D ~ 0.18D.In the embodiment shown in fig. 3, the maximum depth mixing groove 5 is positioned at the conical lower portion of boss 13.
Border corresponding with cylinder wall 3 bottom cylinder head is circular, dotted line as shown in Figure 2.Cylinder head 1 is called fire power face towards the surface of piston 4.As shown in fig. 1, fire power face is essentially smooth.The center of fire power face is provided with the oil sprayer port one 2 for installing oil sprayer 2, and the axis of oil sprayer 2 is vertical with fire power face, and the axis of oil sprayer 2 overlaps with the central axis 10 (as shown in Figure 3) of piston.The end of oil sprayer 2 is provided with multiple spray-hole, and fuel oil penetrates from nozzle opening, and multiply fuel oil can form three-dimensional cone angle, and this cone angle is obtuse angle usually.The quantity of jet hole is no less than five usually.Preferably, multiple nozzle opening is distributed on the end of oil sprayer 2.
As shown in Figure 2, in cylinder head 1, the position corresponding with each cylinder is provided with two air inlet ports 8 and an exhaust port 9.Formation ridge area, region 11 between adjacent air inlet port 8 and between adjacent air inlet port 8 and exhaust port 9, the width T of ridge area 11 is not less than 7mm.Cooling passage can be arranged in the cylinder head inside of corresponding cylinder operation region, and cooling liquid can be cooled the key area of cylinder head, ensures the reliable serviceability temperature of metal temperature lower than them.
Preferably, air inlet port 8 and exhaust port 9 are arranged with certain orientation, to be assisted the running of three valves by single camshaft, three valves are installed in air inlet port 8 and exhaust port 9 after assembling.Alternately, also twin cam shaft cylinder head can be used.
During diesel engine with direct injection work of the present invention, when piston 4 be positioned at or close to oil sprayer 2 during its top dead center position by nozzle opening injected fuel, the spray angle of oil sprayer 2 and the dimensional parameters of mixing groove 5 make the jet of fuel oil depart from boss 13 surface, thus inject fuel in lower recess 15, to extend the holdup time of fuel oil in firing chamber.The air of two air inlet ports 8 rotates rapidly around axis 10 in firing chamber simultaneously, fully mix with the fuel oil in lower recess 15, make fuel oil perfect combustion substantially, and it is very efficient, decrease the amount of uncompleted burned carbon hydrogen compound to the full extent, decrease the generation of carbon soot particles equally to the full extent.Waste gas after burning leaves firing chamber by exhaust port 9.
Relative to two valve diesel, invention increases the charging efficiency of cylinder, the geomery parameter simultaneously by mixing groove comes Optimizing Combustion room, thus improves the burning of diesel engine, effectively improves engine performance and emission level; Three valve be arranged on the internal structure simplifying cylinder head water cavity to a certain extent, guarantee that there are enough layout cooling channels, space the maximum valve ridge area of heat load, decrease manufacture difficulty and manufacture cost while reducing cost of production, and decrease the component of some.
The aforementioned description to concrete exemplary of the present invention is to illustrate and the object of illustration.These descriptions not want the present invention to be defined as disclosed precise forms, and obviously, according to above-mentioned instruction, can much change and change.The object selected exemplary embodiment and describe is to explain certain principles of the present invention and practical application thereof, thus those skilled in the art can be realized and utilize various different exemplary of the present invention and various different selection and change.Scope of the present invention is intended to limited by claims and equivalents thereof.
Claims (9)
1. a diesel engine with direct injection, is characterized in that, described diesel engine with direct injection comprises:
Multiple cylinder, is provided with piston in each described cylinder, and the top of described piston is provided with the mixing groove of the axisymmetrical about described piston, and the cross section of described mixing groove is in " ω " shape, and described mixing groove comprises:
Radial flange, described radial flange is arranged on the middle and upper part of the inwall of described mixing groove;
Lower recess, described lower recess is positioned at the below of described radial flange, the sidewall of described lower recess from top to bottom comprises up-small and down-big tapered portion and arc portion, described tapered portion from described radial flange to downward-extension, the place of bottom centre of described lower recess is provided with boss, described boss is frusto-conical, and the end face of described boss and the lower end of described tapered portion are in same horizontal plane, and described arc portion is folded between the bottom of described boss and the lower end of described tapered portion; And
Upper grooves, described upper grooves is positioned at the top of described radial flange, and the diameter of described upper flange increases to the end face of described piston gradually from described radial flange; And
Cylinder head, described cylinder head is provided with the oil sprayer corresponding with each described cylinder, the axis of described oil sprayer and the central axes of described piston, the uniform multiple nozzle opening in end of described oil sprayer, the fuel oil of described multiple nozzle opening ejection is injected in described lower recess; Position corresponding with each described cylinder in described cylinder head is provided with two air inlet ports and an exhaust port.
2. diesel engine with direct injection according to claim 1, is characterized in that, the three-dimensional cone angle that the injection direction of described multiple nozzle opening ejection is formed is obtuse angle.
3. diesel engine with direct injection according to claim 1, it is characterized in that, the maximum diameter of described upper grooves is 0.61 ~ 0.71 times of the diameter of described piston, the diameter of described radial flange is 0.5 ~ 0.6 times of the diameter of described piston, and the maximum diameter of described lower recess is 0.56 ~ 0.60 times of the diameter of described piston.
4. diesel engine with direct injection according to claim 3, it is characterized in that, the maximum depth of described mixing groove is 0.15 ~ 0.18 times of the diameter of described piston, described upper grooves the degree of depth be 0.02 ~ 0.05 times of the diameter of described piston, the distance of the top of described boss and the end face of described piston is 0.05 ~ 0.09 times of the diameter of described piston.
5. diesel engine with direct injection according to claim 4, is characterized in that, the angle of described boss is 110 ° ~ 130 °.
6. diesel engine with direct injection according to claim 1, is characterized in that, the formation ridge area, region between adjacent described air inlet port and between adjacent air inlet port and described exhaust port, the width of described ridge area is not less than 7mm.
7. diesel engine with direct injection according to claim 1, is characterized in that, described cylinder head is single camshaft cylinder head.
8. diesel engine with direct injection according to claim 1, is characterized in that, described cylinder head is twin cam shaft cylinder head.
9. diesel engine with direct injection according to claim 1, is characterized in that, described cylinder head surface is smooth to the surface of described piston.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510307298.5A CN104879233A (en) | 2015-06-08 | 2015-06-08 | Direct-injection type diesel engine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510307298.5A CN104879233A (en) | 2015-06-08 | 2015-06-08 | Direct-injection type diesel engine |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN104879233A true CN104879233A (en) | 2015-09-02 |
Family
ID=53946873
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201510307298.5A Pending CN104879233A (en) | 2015-06-08 | 2015-06-08 | Direct-injection type diesel engine |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN104879233A (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| 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 |
| CN114810412A (en) * | 2022-05-20 | 2022-07-29 | 潍柴动力股份有限公司 | Piston and gas engine |
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| CN204663692U (en) * | 2015-06-08 | 2015-09-23 | 广西玉柴机器股份有限公司 | A kind of diesel engine with direct injection |
-
2015
- 2015-06-08 CN CN201510307298.5A patent/CN104879233A/en active Pending
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Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| 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 |
| CN111287860B (en) * | 2020-05-13 | 2020-09-29 | 潍柴动力股份有限公司 | Weak tumble fast combustion system and gas engine |
| US11149680B1 (en) | 2020-05-13 | 2021-10-19 | Weichai Power Co., Ltd. | Weak tumble flow fast combustion system and gas engine |
| CN114810412A (en) * | 2022-05-20 | 2022-07-29 | 潍柴动力股份有限公司 | Piston and gas engine |
| CN114810412B (en) * | 2022-05-20 | 2024-04-16 | 潍柴动力股份有限公司 | Piston and gas engine |
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Application publication date: 20150902 |