• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    A spark-ignition, air-compressing internal combustion engine has a combustion chamber in a piston movable toward a cylinder head of the engine. Fuel is injected onto the wall of the combustion chamber and air rotated in the chamber to remove the fuel from the combustion chamber wall gradually as a vapor. The cross-section of the combustion chamber wall is defined by two curved lines of specific radial relation generally indicated by the curved line extending from the opening into the combustion chamber having the smaller radius of curvature.
    公开号:SU1237090A3
    申请号:SU833670651
    申请日:1983-12-09
    公开日:1986-06-07
    发明作者:Хмела Франц；Херцог Вальтер；Майер Рихард
    申请人:М.А.Н.Машиненфабрик Аугсбург-Нюрнберг Аг (Фирма)；
    IPC主号:
    专利说明:

    2. The engine according to claim 1, of which the middle part of the combustion chamber is designed in the form of a dome-shaped elevation.
    3. The motor according to claim 1, 2, and t — and the fact that the axis of the nozzle channel forms an angle jb equal to 10–15 with the plane perpendicular to the cylinder axis; the intersection point of the channel axis with the wall of the combustion chamber is in the upper position the piston dead center is below the piston bottom by an amount AO-60% of the depth of the combustion chamber,
    4. The motor on the PP, 1 and 2, which repeats with the fact that the dental angle is L. between the intersection point of the axis of the nozzle channel with the wall of the combustion chamber and the center of the ignition device in the plane, perpendicular pf
    The invention relates to mechanical engineering, and. to the design of the engines of internal combustion.
    The purpose of the invention is to increase the efficiency of the engine.
    Fig. I shows the proposed engine, a longitudinal section; figure 2 - the same cross section.
    The engine contains a cylinder head 1 with nozzles 2 placed in it and an ignition device 3, a piston 4 in which the combustion chamber 5 is located, made in the form of a body of rotation, the side wall of the combustion chamber 5 in cross section is formed by a straight line section 6 and two curved lines 7 and 8 into each other, line 7 being made with a smaller radius of curvature R (and extending from the straight line section 6 to the largest diameter of the DJ combustion chamber 5, the other line 8 being made with a larger curvature radius R and extending from and a larger diameter Dj. of the combustion chamber 5 to its bottom 9, on which a dome-shaped elevation can be performed; the largest diameter of the DJ combustion chamber 5
    axis of the cylinder, is made equal to 15-45.
    5, the engine of claim.
    This is due to the fact that the ignition device consists of two pairs of alleles to one another of the 3 Z electrodes.
    6. The engine on the PP. 1-4, which is the fact that the electrode of one pole consists of several electrodes surrounding the rod electrode of the other pole.
    7 "Engine according to claim 1, characterized in that the ignition device is in the form of a glow plug.
    8 “Engine 1, distinguished by the fact that the ignition device is located in the combustion chamber at the position of porgan in the top dead center at a depth of 12 mm.

    made equal to 0.5-0.7 of the diameter Dj of the piston and is located at depths; HI equal to 0.3-0.4 of the depth H of the combustion chamber 5, the smaller radius of curvature R, is equal to (0.2-0.3) H, and the larger radius of curvature R рг1вен (О, 5-0.75) Н , the ratio of the diameter of the neck d of the combustion chamber 5 to D is equal to 0.85-0.95, and the length of the rectilinear segment 6 is hj and (0.1-0.15) H. The canasta axis of the nozzle 2 forms an angle 1 ,, perpendicular to the cylinder axis, equal to 10-15, and the intersection point A of the extended axis of the channel from the spray point B from the wall of the combustion chamber 5 (in the position of the upper dead point of the piston 4) is below the bottom dead center ; and 10 piston 4 on the value of h, equal to 40-60% of the depth H of the combustion chamber 5.
    The central angle c1 between the point A of the intersection of the axis of the nozzle channel with the wall of the combustion chamber 5 and the center of the ignition device 3 in a plane perpendicular to the axis of the cylinder is 15–45 °. The 3rd ignition may consist of m1 of two parallel to one another step3
    new electrodes, and one of the rod electrodes can be made in the form of several electrodes I1, surrounding the electrode 12 of the other pole.
    The ignition device 3 can be made in the form of a glow plug and is located in the combustion chamber 5 with the piston in the top dead center at a depth of 12 mm.
    During engine operation, fuel is supplied through nozzle 2 to combustion chamber 5 and, in accordance with the chosen specific shape of the combustion chamber, is concentrated in a special zone that is located in the neck area of the combustion chamber 5, thereby providing the electrodes of the ignition device 3 ready to
    ignition of the fuel mixture. Increased -20 fuel) low boiling point, co-diameter D, combustion chamber 5 improves the use of air, as the proportion of fresh air between the bottom 10 of the piston 4 and the cylinder head I decreases, and the opposite side 5 of the combustion chamber 5 is closer to the nozzle 2 whereby the height of the nozzle in the chamber 5 of the piston 4 is shortened.
    With a strong concentration of the fuel-air mixture in the region of the largest diameter D of the combustion chamber 5, the spark gap is supplied with a combustible fuel mixture 35, which makes it unnecessary to use, for example, an inlet groove that must conduct the liquid fuel before the spark gap. This improvement in gas exchange makes it possible for 40 to reduce the Required ignition energy, since this results in a higher local concentration of the fuel mixture, which is proportional to the ionization voltage, as well as the duration of the spark. Due to the small distance between the largest diameter of the combustion chamber 5 and the neck of the chamber, short electrodes are needed, which have the advantage, consistency, and evaporation, and thereby slowing down the swirling flow in the region of the largest diameter D of the combustion chamber 5, compared with the spherical combustion chamber, having a much smaller diameter.
    The implementation of the middle part of the bottom 9 of the combustion chamber 5 in the form of a dome-shaped return contributes to the combustion process.
    Due to the decrease in the depth H of the combustion chamber 5, i.e. Because of the larger diameter D, the combustion chamber, or the larger diameter d of its neck, the fuel jet is injected with a slight curvature. At the same time, the jet of fuel forms with the plane perpendicular to the axis of the cylinder, the angle / i equal to 10-15. Injection occurs in this way at the start of injection at full load, approximately at the crankshaft angle of rotation to the top dead center), that when injection occurs, the fuel never reaches the bottom of the piston, point A hits the fuel jet on the wall of the combustion chamber the piston is not too deep in the lower region of the combustion chamber.

    370904
    longer in service life, since they remain cooler, not least because of the slight movement of air that is available. This makes it possible to raise the degree of compression above 18 without fear of an unacceptable increase in the proportion of burn caused by the level of pressure and temperature in the cylinder associated with this degree of compression and thereby the heat load on the electrodes of the ignition device 3.
    The combustion chamber of the proposed design is convenient when using an engine with forced ignition, since the fuel (for example, methanol) necessary for this process has (as a diesel)
    ten
    15
    consequently, the slowing down of the swirling flow in the region of the largest diameter D of the combustion chamber 5 as compared with a spherical combustion chamber having a much smaller diameter.
    The implementation of the middle part of the bottom 9 of the combustion chamber 5 in the form of a dome-shaped return contributes to the combustion process.
    Due to the decrease in the depth H of the combustion chamber 5, i.e. Because of the larger diameter D, the combustion chamber, or the larger diameter d of its neck, the fuel jet is injected with a slight curvature. At the same time, the jet of fuel forms with the plane perpendicular to the axis of the cylinder, the angle / i equal to 10-15. Injection occurs in this way at the start of injection at full load, approximately at the crankshaft angle of rotation to the top dead center), that when injection occurs, the fuel never reaches the bottom of the piston, point A hits the fuel jet on the wall of the combustion chamber the piston is not too deep in the lower region of the combustion chamber.
    Phage1
    权利要求:
    Claims (8)
    [1]
    1. INTERNAL COMBUSTION ENGINE with air compression, positive ignition and direct fuel injection, containing a cylinder head with a nozzle and an ignition device placed in it, a cylinder with a piston placed in it, in which a combustion chamber made in the form of a body of revolution is located, the side wall of the chamber combustion in cross section is formed by a straight section located from the piston bottom, and two curved lines passing one into another, the first line being made with a smaller radius cr visas and passes from a straight section to the largest diameter of the combustion chamber, and the second line is made with a large radius of curvature and passes from the largest diameter of the combustion chamber to its bottom, characterized in that, in order to increase efficiency, the largest diameter of the combustion chamber is made equal to 0.5 -0.7 diameter of the piston and is located from the piston bottom at a depth equal to 0.30.4 of the depth of the combustion chamber, the smaller radius of curvature of the side wall of the combustion chamber is made 0 ', 2-0.3 of its depth, and the larger radius is 0, 5-0.75, the ratio of diameter the combustion chamber throat to its largest diameter is equal to 0.85-0.95, and the length of the straight section of the combustion chamber is equal to the depth of 0.1-0.15 latter.
    SU <, ”1237090
    [2]
    2. The engine according to claim 1, with the fact that the middle part of the combustion chamber is made in the form of a domed elevation.
    [3]
    3. The engine according to claim 1, wherein the axis of the nozzle channel forms an angle β equal to 10-15 ° with the plane perpendicular to the cylinder axis, and the point of intersection of the channel axis with the wall of the combustion chamber at top dead center the piston is located below the piston bottom by an amount equal to 40-60% of the depth of the combustion chamber.
    [4]
    4. The engine popp-1 and 2, with the fact that the dental angle between the point of intersection of the axis of the nozzle channel with the wall of the combustion chamber and the center of the ignition device in a plane perpendicular to the cylinder axis 123 is made equal to
    15-45 °.
    [5]
    5. The engine according to claim 1, o tl and - wherein the ignition device consists of two rod Z. spectrodes parallel to one another.
    [6]
    6. The engine according to paragraphs. 1-4, characterized in that the electrode of one pole consists of several electrodes surrounding the rod electrode of the other pole.
    [7]
    7. Engine pop. 1, characterized in that the ignition device is made in the form of a glow plug.
    [8]
    8 “Engine 1., distinguished by the fact that the ignition device is located in the combustion chamber with the piston at top dead center at a depth of 12 mm.
    ί
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    同族专利:
    公开号 | 公开日
    NZ206528A|1986-07-11|
    AU563967B2|1987-07-30|
    SE8306390L|1984-06-11|
    BR8306933A|1984-07-24|
    DD230899A1|1985-12-11|
    IN158545B|1986-12-06|
    AT396509B|1993-10-25|
    IT8324065D0|1983-12-06|
    FR2537651B1|1992-04-03|
    US4492194A|1985-01-08|
    JPH0218408B2|1990-04-25|
    ZA839177B|1984-08-29|
    GB2134975A|1984-08-22|
    GB8332667D0|1984-01-11|
    AR230098A1|1984-02-29|
    FR2537651A1|1984-06-15|
    GB2134975B|1986-01-29|
    KR920006541B1|1992-08-08|
    AU2227783A|1984-06-14|
    SE456263B|1988-09-19|
    CA1209427A|1986-08-12|
    ATA429483A|1993-01-15|
    IT1194503B|1988-09-22|
    DE3245780C1|1983-12-29|
    JPS59150923A|1984-08-29|
    KR840007135A|1984-12-05|
    SE8306390D0|1983-11-18|
    NL8304075A|1984-07-02|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    GB531910A|1938-07-13|1941-01-14|Lancia Automobili|Improvements in or relating to internal combustion engines operating with injection of liquid fuel into the cylinders|
    GB643351A|1946-09-06|1950-09-20|Antonin Zelezny|Arrangement of the combustion space and the injection nozzle in internal combustion engines|
    US2921566A|1955-06-10|1960-01-19|Maschf Augsburg Nuernberg Ag|Internal combustion engine and method of operating it|
    US2942591A|1957-05-21|1960-06-28|Maschf Augsburg Nuernberg Ag|Piston|
    GB967126A|1962-12-06|1964-08-19|John Peter Hindley|Improvements in internal combustion engines|
    DE1576020A1|1967-09-22|1970-04-02|Maschf Augsburg Nuernberg Ag|Externally ignited air-compressing internal combustion engine|
    CH478343A|1967-09-22|1969-09-15|Maschf Augsburg Nuernberg Ag|Spark ignition, air-compressing injection internal combustion engine|
    DE2038048C3|1970-07-31|1975-06-19|Maschinenfabrik Augsburg-Nuernberg Ag, 8500 Nuernberg|Air-compressing, direct-injection internal combustion engine|
    DE2424514A1|1974-05-20|1975-12-04|Daimler Benz Ag|Four stroke piston engine with external ignition - fuel is injected earlier on load than on slow running|
    DE2611624C2|1976-03-19|1982-06-03|M.A.N. Maschinenfabrik Augsburg-Nürnberg AG, 8500 Nürnberg|Externally ignited, air-compressing internal combustion engine|
    DE2815717A1|1977-04-29|1978-11-02|List Hans|AIR COMPRESSING, DIRECT INJECTING COMBUSTION ENGINE|
    JPS6056893B2|1977-12-09|1985-12-12|Isuzu Motors Ltd|
    DE2755916C2|1977-12-15|1982-07-08|M.A.N. Maschinenfabrik Augsburg-Nürnberg AG, 8500 Nürnberg|Method for burning externally igniting fuels in an air-compressing, direct-injection internal combustion engine|
    US4203393A|1979-01-04|1980-05-20|Ford Motor Company|Plasma jet ignition engine and method|JPS601323A|1983-06-16|1985-01-07|Toyota Motor Corp|Cylinder fuel injection type spark ignition internal- combustion engine|
    AU586595B2|1985-11-30|1989-07-13|Isuzu Motors Limited|Combustion chamber arrangement for an internal combustion engine|
    DE3632579C2|1986-09-25|1990-07-12|Man Nutzfahrzeuge Ag, 8000 Muenchen, De|
    EP0369480A3|1988-11-18|1991-01-02|Toyota Jidosha Kabushiki Kaisha|An internal combustion engine|
    US5109816A|1990-04-27|1992-05-05|Toyota Jidosha Kabushiki Kaisha|Direct fuel injection type spark ignition internal combustion engine|
    US5115774A|1990-12-26|1992-05-26|Toyota Jidosha Kabushiki Kaisha|Internal combustion engine|
    JPH1082323A|1996-09-06|1998-03-31|Mitsubishi Motors Corp|Combustion chamber of diesel engine|
    GB2330177A|1997-10-09|1999-04-14|Ford Global Tech Inc|Prevention of auto-ignition in end gas regions of a cylinder of a gasoline spark-ignition i.c engine|
    JPH11190217A|1997-10-20|1999-07-13|Nissan Motor Co Ltd|Direct injection type diesel engine|
    JPH11182249A|1997-12-18|1999-07-06|Nissan Motor Co Ltd|Direct injection spark-ignition type internal combustion engine|
    DE10033597C2|2000-07-11|2003-12-11|Daimler Chrysler Ag|Method for operating a diesel engine|
    DE10331267A1|2003-07-10|2005-02-03|Robert Bosch Gmbh|fuel injection system|
    FR2910054A1|2006-12-15|2008-06-20|Renault Sas|Spark ignition internal combustion engine, has spark plugs projecting into combustion chamber, where shape of chamber, position of plug and compression ratio are determined such that combustion is raced after triggering of engine|
    WO2011043399A1|2009-10-06|2011-04-14|イマジニアリング株式会社|Internal combustion engine|
    US9429101B2|2013-08-21|2016-08-30|Caterpillar Inc.|Combustion engine piston and engine using same|
    AT17205U1|2020-06-18|2021-09-15|Innio Jenbacher Gmbh & Co Og|Pistons for internal combustion engine and internal combustion engine with such|
    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    DE3245780A|DE3245780C1|1982-12-10|1982-12-10|Externally ignited, air compressing internal combustion engine|
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