CN105840293B - For the squish flow combustion system of opposed-piston engine - Google Patents
For the squish flow combustion system of opposed-piston engine Download PDFInfo
- Publication number
- CN105840293B CN105840293B CN201610206148.XA CN201610206148A CN105840293B CN 105840293 B CN105840293 B CN 105840293B CN 201610206148 A CN201610206148 A CN 201610206148A CN 105840293 B CN105840293 B CN 105840293B
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- Prior art keywords
- combustion chamber
- squish flow
- room
- piston
- opposed
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Classifications
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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
- F02B23/02—Other engines characterised by special shape or construction of combustion chambers to improve operation with compression ignition
- F02B23/06—Other engines characterised by special shape or construction of combustion chambers to improve operation with compression ignition the combustion space being arranged in working piston
- F02B23/0618—Other engines characterised by special shape or construction of combustion chambers to improve operation with compression ignition the combustion space being arranged in working piston having in-cylinder means to influence the charge motion
- F02B23/0621—Squish flow
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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
- F02B23/02—Other engines characterised by special shape or construction of combustion chambers to improve operation with compression ignition
- F02B23/06—Other engines characterised by special shape or construction of combustion chambers to improve operation with compression ignition the combustion space being arranged in working piston
- F02B23/0618—Other engines characterised by special shape or construction of combustion chambers to improve operation with compression ignition the combustion space being arranged in working piston having in-cylinder means to influence the charge motion
- F02B23/063—Other engines characterised by special shape or construction of combustion chambers to improve operation with compression ignition the combustion space being arranged in working piston having in-cylinder means to influence the charge motion the combustion space in the piston interacting fluid dynamically with the cylinder head, the injector body or the cylinder wall
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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
- F02B23/02—Other engines characterised by special shape or construction of combustion chambers to improve operation with compression ignition
- F02B23/06—Other engines characterised by special shape or construction of combustion chambers to improve operation with compression ignition the combustion space being arranged in working piston
- F02B23/0678—Unconventional, complex or non-rotationally symmetrical shapes of the combustion space, e.g. flower like, having special shapes related to the orientation of the fuel spray jets
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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
-
- 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
-
- 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
Abstract
The present invention relates to a kind of combustion systems of internal combustion engine, and in particular to the combustion chamber of a variety of opposed-piston engines.For the squish flow combustion system of opposed-piston engine, including：Fuel injector (3), inlet piston (4), exhaust pition (5)；Its technical solution is, inlet piston (4) and the containing room (2) that spindle-type is symmetrically equipped on exhaust pition (5), the region formed between inlet piston (4) and exhaust pition (5) opposite face are squish flow room (1).The present invention passes through on the basis of flat spherical combustion chamber, increase squish flow room, and piston-top surface is designed to spindle-type α-Fe2O3 by the distribution according to oily beam, to improve the utilization rate of air, so as to make full use of the air in the entire space in combustion chamber, improve engine economy, dynamic property and emission performance.
Description
Technical field
The present invention relates to a kind of combustion systems of internal combustion engine, and in particular to the combustion system of a variety of opposed-piston engines.
Background technology
Opposed-piston diesel can effectively improve combustibility and emission performance.It is opposed compared with conventional diesel engine
Piston diesel engine distinct issues are still the distribution, diffusion and mixing of fuel oil.It improves the utilization rate of the bags, accelerate combustion
The mixing velocity of oil and air can effectively improve the dynamic property, economy and emission performance of diesel engine.
It generally using flat ball shape structure such as Fig. 1 (a, c), is tied including combustion chamber the combustion chamber of existing opposed-piston diesel
Structure and injection system, combustion chamber are the spaces surrounded by the top surface and cylinder wall of two pistons.Existing flat spherical combustion chamber category
In containing type combustion chamber, the purpose of design is the contour line envelope fuel injection pattern by combustion chamber, so that in combustion chamber
Air it is as much as possible be distributed in around fuel spray, improve the indoor air utilization ratio of burning.It is right as shown in Fig. 1 (b)
The injection system of opposed duel fuel injector is used in opposed-piston engine, mist of oil is in spindle-type, and combustion chamber is divided into A areas by mist of oil
With B areas.A areas are the central area of combustion chamber, and B is the fringe region of combustion chamber.From figure 1 it appears that the volume of B area is about
Account for the 0.25~0.5 of combustion chamber volume.Since opposed-piston diesel sprays point for causing oily beam in axial cross section from side
Cloth range is generally 0 °~60 °, thus the air utilization ratio of B area is caused to decline.
Invention content
The purpose of the present invention is：Contain the structure of room and squish flow room by design, the air for improving combustion chamber B area utilizes
Rate accelerates the mixing velocity of fuel oil and air, improves the combustion process of opposed-piston engine with this.
The technical scheme is that：Include for the squish flow combustion system of opposed-piston engine：Fuel injector, air inlet are lived
Plug, exhaust pition；Inlet piston and the containing room that spindle-type is symmetrically equipped on exhaust pition, inlet piston and exhaust pition phase
The region formed between opposite is squish flow room, and the both ends that two fuel injectors are set to spindle-type and contain room in 180 °, two spray
The oily beam of oily device ejection is angled to be interspersed.
Advantageous effect:The present invention is by the basis of flat spherical combustion chamber, increasing squish flow room, and according to the distribution of oily beam
Piston-top surface is designed to spindle-type α-Fe2O3, to improve the utilization rate of air, so as to make full use of in the entire space in combustion chamber
Air improves engine economy, dynamic property and emission performance.
Description of the drawings
Fig. 1 is existing oblate spheroid type combustion system and its piston schematic diagram；
Fig. 2 is squish flow stream combustion system provided by the invention and its piston schematic diagram；
Fig. 3 is flat spherical combustion chamber and squish flow combustion chamber indicated horsepower comparison diagram；
Fig. 4 is average pressure curve in flat spherical combustion chamber and squish flow combustion chamber cylinder；
Fig. 5 is mean temperature curve in flat spherical combustion chamber and squish flow combustion chamber cylinder；
Fig. 6 is flat spherical combustion chamber and squish flow combustion chamber instantaneous heating rate curve；
Fig. 7 is flat spherical combustion chamber and squish flow combustion chamber cumulative heat release curve；
Fig. 8 is flat spherical combustion chamber and squish flow combustion chamber Soot mass fraction correlation curves.
Specific embodiment
Embodiment, referring to attached drawing 2, for the squish flow combustion system of opposed-piston engine, including：Fuel injector 3, air inlet are lived
Plug 4, exhaust pition 5；Inlet piston 4 and the containing room 2 that spindle-type is symmetrically equipped on exhaust pition 5, inlet piston 4 and exhaust
The region formed between 5 opposite face of piston is squish flow room 1, and two fuel injectors 3 are set to the two of spindle-type containing room 2 in 180 °
End.1 one side of squish flow room that the present invention designs reduces the space that cannot be made full use of, and on the other hand the structure contributes to squish flow
Generation, so as to which the gas in cylinder be promoted to flow, accelerate air-fuel mixture and burning.Since the containing room 2 of spindle-type is further
The space of the injection of fuel oil is limited, therefore when matching atomizer, it is larger that the direction of spray orifice should be distributed in space as far as possible
Radial direction interface, oily beam should be interspersed at an angle, so as to be conducive to being uniformly distributed for oil gas.
Combustion chamber is caused to play maximum effect, this requires the appropriate matchings in oil, gas, room.Squish flow room 1 helps speed up
The flowing of air, however when squish flow room 1 is bigger than normal, it will so that the space for containing room 2 is less than normal, so that Fuel beam distribution weighs
The phenomenon that overlapping mistake is unfavorable for the diffusion of fuel oil.When squish flow room 1 is less than normal, and the air that can to contain in room 2 cannot be fully
It utilizes.Contain room 2 and the distribution of fuel spray is closely related, the fusellal fabric structure for containing room 2 must be appropriate with injection mode
Ground matches.Therefore the structure for containing room and the ratio for containing room and squish flow room should rationally be determined.
The size of containing room is in the present embodiment：The a diameter of D, clearance δ of inlet piston 4 and exhaust pition 5；Contain room
2：Height H=(0.091~0.121), width L=(0.379~0.606) D, a=25 ° of spindle-type angle~30 °；Squish flow room 1：
Height H1=δ+(0.015~0.023) D.
Contain the volume ratio V of room 2 and squish flow room 11/V2=0.13~0.35, the size and oily beam for containing room 2 also have closely
Relationship, when oily beam is more, containing room will suitably tune up；When oily beam is less, containing room will suitably turn down.
The CFD three-dimensional grid models of the squish flow combustion chamber under the conditions of identical compression ratio and flat spherical combustion chamber are established respectively,
Simulation calculation comparison is carried out, the two kinds of combustion chambers established in three-dimensional modeling under the conditions of almost equal grid are calculated to be subject to
Compare, other calculating and settings are identical.Thus the indicated horsepower of flat spherical combustion chamber and squish flow combustion chamber is obtained, mean pressure in cylinder
Mean temperature in power, cylinder, instantaneous heating rate, Cumulative heat release, Soot mass fractions comparison diagram.
Wherein Fig. 3 is flat spherical combustion chamber and squish flow combustion chamber indicated horsepower comparison diagram.Be computed, from inlet close to
In the calculating period of Exhaust Open, the indicated horsepower of squish flow combustion chamber and flat spherical combustion chamber be respectively 72.03kW and
71.43kW, the flat spherical combustion chamber of power ratio of squish flow combustion chamber are high by 0.84%.
Fig. 4 tries hard to for mean pressure in flat spherical combustion chamber and squish flow combustion chamber cylinder.It can be seen from the figure that squish flow combustion chamber
Average pressure can reach 72.8bar in most vat, and flat spherical combustion chamber is 70.2bar.In entire combustion process, squish flow combustion
It is higher than average pressure in flat spherical combustion chamber cylinder to burn average pressure in the cylinder of room.
Fig. 5 is mean temperature figure in flat spherical combustion chamber and squish flow combustion chamber cylinder.It can be seen from the figure that before 175 °C of A
Mean temperature is not much different in cylinder, and during 175 °C of A to 225 °C of A, squish flow combustion chamber mean temperature is higher than flat spherical combustion chamber, but
Its mean temperature of burning illustrates that burning early period of squish flow combustion chamber is fast less than flat spherical combustion chamber after 225 °C of A.
Fig. 6 and Fig. 7 is respectively the instantaneous heating rate and Cumulative heat release curve of two kinds of combustion chambers.It is flat at combustion heat release initial stage
The burning instantaneous heating rate of spherical combustion chamber is basically identical, and the heat release of squish flow combustion chamber comparatively fast occurs higher than flat since 172 °C of A
The exothermic peak of spherical combustion chamber.There is higher combustion heat release in subsequent squish flow combustion chamber within 176 °C of A to 190 °C of A this periods
Rate makes it on cumulative heat release higher than flat spherical combustion chamber, and squish flow combustion chamber is fired more than oblate spheroid type from cumulative heat release
Burn room.
Fig. 8 is the Soot mass fraction curves of two kinds of combustion chambers, it can be seen from the figure that in entire combustion process,
The Soot of squish flow combustion chamber discharge is lower than the Soot that flat spherical combustion chamber discharges, and illustrates that squish flow combustion chambers burn is more abundant, arranges
It puts relatively low.
Claims (2)
1. for the squish flow combustion system of opposed-piston engine, including：Fuel injector (3), inlet piston (4), exhaust pition
(5)；It is characterized in that, containing room (2) of the inlet piston (4) with being symmetrically equipped with spindle-type on the exhaust pition (5),
The region formed between the inlet piston (4) and the exhaust pition (5) opposite face is squish flow room (1)；Two sprays
The both ends that oily device (3) is set to the spindle-type and contains room (2) in 180 °, the oily beam that two fuel injectors (3) spray are in angle
Degree is interspersed；
The inlet piston (4) and a diameter of D, clearance δ, described containing room (2) height H=of the exhaust pition (5)
(0.091~0.121) D, width L=(0.379~0.606) D, a=25 ° of spindle-type angle~30 °；The squish flow room (1) is high
Spend H1=δ+(0.015~0.023) D.
2. it to be used for the squish flow combustion system of opposed-piston engine as described in claim 1, which is characterized in that the containing room
(2) with volume ratio V1/V2=0.13~0.35 of the squish flow room (1).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201610206148.XA CN105840293B (en) | 2016-04-05 | 2016-04-05 | For the squish flow combustion system of opposed-piston engine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201610206148.XA CN105840293B (en) | 2016-04-05 | 2016-04-05 | For the squish flow combustion system of opposed-piston engine |
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| Publication Number | Publication Date |
|---|---|
| CN105840293A CN105840293A (en) | 2016-08-10 |
| CN105840293B true CN105840293B (en) | 2018-06-29 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201610206148.XA Active CN105840293B (en) | 2016-04-05 | 2016-04-05 | For the squish flow combustion system of opposed-piston engine |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN115163293B (en) * | 2022-06-30 | 2023-08-18 | 北京理工大学 | Rolling flow-extrusion flow-rolling flow synergistic rapid combustion optimization method for natural gas engine |
Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB218000A (en) * | 1923-03-28 | 1924-06-30 | Robert Pile Doxford | Improvements in or relating to engines operated by liquid-fuel |
| US1523453A (en) * | 1918-06-18 | 1925-01-20 | Super Diesel Tractor Corp | Combustion chamber for liquid-fuei engines |
| DE102004010361A1 (en) * | 2003-03-05 | 2004-12-30 | Otte, Dirk | Counter piston engine with piston temperature equalization function relocates thermal load in engine by combustion procedure for bearing of inlet piston in engine to equalize piston temperature |
| CN102947545A (en) * | 2010-04-27 | 2013-02-27 | 阿凯提兹动力公司 | Combustion chamber constructions for opposed-piston engines |
| CN103562515A (en) * | 2011-05-18 | 2014-02-05 | 阿凯提兹动力公司 | Combustion chamber construction for opposed-piston engines |
| CN105422257A (en) * | 2015-12-14 | 2016-03-23 | 中国北方发动机研究所(天津) | Double w-shaped combustion chamber applicable to opposed injection |
| CN105422258A (en) * | 2015-12-14 | 2016-03-23 | 中国北方发动机研究所(天津) | Double T-shaped combustion chamber applicable to opposed injection |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB2493260A (en) * | 2011-07-26 | 2013-01-30 | Ecomotors Internat Inc | Opposed piston engine with tumble flow in shaped combustion chamber |
-
2016
- 2016-04-05 CN CN201610206148.XA patent/CN105840293B/en active Active
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US1523453A (en) * | 1918-06-18 | 1925-01-20 | Super Diesel Tractor Corp | Combustion chamber for liquid-fuei engines |
| GB218000A (en) * | 1923-03-28 | 1924-06-30 | Robert Pile Doxford | Improvements in or relating to engines operated by liquid-fuel |
| DE102004010361A1 (en) * | 2003-03-05 | 2004-12-30 | Otte, Dirk | Counter piston engine with piston temperature equalization function relocates thermal load in engine by combustion procedure for bearing of inlet piston in engine to equalize piston temperature |
| CN102947545A (en) * | 2010-04-27 | 2013-02-27 | 阿凯提兹动力公司 | Combustion chamber constructions for opposed-piston engines |
| CN103562515A (en) * | 2011-05-18 | 2014-02-05 | 阿凯提兹动力公司 | Combustion chamber construction for opposed-piston engines |
| CN105422257A (en) * | 2015-12-14 | 2016-03-23 | 中国北方发动机研究所(天津) | Double w-shaped combustion chamber applicable to opposed injection |
| CN105422258A (en) * | 2015-12-14 | 2016-03-23 | 中国北方发动机研究所(天津) | Double T-shaped combustion chamber applicable to opposed injection |
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| CN105840293A (en) | 2016-08-10 |
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