• 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:
    The invention relates to a piston (1) of an internal combustion engine and a use thereof for an Otto Mo tor with external mixture formation. A piston skirt (1.1) can have a center axis M and a piston skirt (2) which delimits the piston skirt (1.1) with a diameter D. The piston crown (2) can consist of a piston bottom edge (2.1) of width b and a piston depression (2.2) be formed a depth t. The piston recess (2.2) can be formed as a pot well and has a piston bowl bottom (3) and an adjoining piston bowl wall (4) with a maximum diameter d4. The piston bowl (2.2) may have a symmetrical to the central axis M directed from opening cross section A with a minimum diam ser da, which is smaller than the diameter d4. Due to the reduced diameter there may be formed as a nose torn-off edge (5) in the region of the opening cross-section A. The nose (5) can protrude in the radial direction over the piston bowl wall (4) inwardly.
    公开号:AT514638A2
    申请号:T9148/2013
    申请日:2013-04-12
    公开日:2015-02-15
    发明作者:
    申请人:Caterpillar Energy Solutions Gmbh；
    IPC主号:
    专利说明:

    Technical area
    The invention relates to a piston of an internal combustion engine with a central axis M having a piston skirt and the piston skirt upwardly bounding piston head with a diameter D, wherein the piston head is formed from a piston bottom edge of the width b and a piston recess with a depth t, wherein the Piston well is designed as a pot well and has a piston bowl bottom and an adjoining piston bowl wall with a diameter d4 and the piston recess a symmetrical to the central axis M aligned opening cross-section A with a diameter there that is smaller than the diameter d4 and by the reduced diameter da as a Nose trained stall-edge is formed in the region of the opening cross section A, wherein the nose protrudes in the radial direction over the piston bowl wall inwardly.
    The invention further relates to a use of a piston having a central axis M and a piston head, which is formed from a piston bottom edge and a piston recess, wherein the piston recess is formed as Topfmulde and adjacent to a Kolbenmuldenboden piston bowl wall having a maximum diameter d4.
    background
    From DE 33 02 427 C2, a piston for a diesel engine with a cup-shaped piston recess is known. In the transition region between the opening cross-section and the other piston bowl wall a sharp edge is provided.
    A similar design is known from DE 31 15 933 Al also for diesel engines, wherein the edge web having gutter causes a swirling within the piston recess, which counteracts the ascending fuel on the wall.
    In the gasoline engine pistons are used with different Kolbenmuldenformen. As a rule, a distinction is made between the following conventional variants: A) Piston with a roof-shaped piston crown. The piston crown is designed for combustion processes with gas-rinsed pre-chamber so that the torch jets hit the combustion chamber walls as late as possible. B) piston with trough-shaped piston bottom. The piston crown is designed so that a Tumbleströmung generated on the inlet side is maintained. C) Piston with omega piston recess. The piston crown is designed for diesel operation for optimal direct injection and is used unchanged in the gasoline engine. The latter for reasons of cost and simplicity, but regardless of a possibly worse combustion process. D) Piston with pot-piston recess and straight piston bowl walls. The piston crown is designed in such a way that a squish flow (squish flow) occurs in the radial direction between the edge of the piston and the cylinder head. In addition, the swirl flow is amplified in the cylindrical pot-piston recess. For engines with swirl inlet channels and chamber candles pistons with pot piston recesses are very well suited. During the compression stroke, the mixture above the piston bottom edge (squish edge) of the piston is displaced into the pot piston recess. During the expansion stroke, the mixture is sucked out of the pot piston recess again. This process leads in particular near the top dead center to strong squish flows.
    In addition to the squish flow, the pot piston recess also leads to an acceleration of the swirl flow generated on the inlet side. Due to the angular momentum conservation, the rotational speed of the swirl flow increases when the mixture is displaced inwardly into the pot piston recess.
    So that a strong squish flow can be generated, the opening cross-section A of the piston crown should be as low as possible. However, this requirement leads to deep wells that can only be realized with difficulty for reasons of strength and space.
    A piston head may be formed such that a squish flow is converted to turbulence as high as possible. For gas engines with external mixture formation, however, the influencing factors were not known. However, the edges known in the prior art at the edge of the piston recess are too far out. Therefore, they are relatively hot, which can lead to pre-ignition especially in gas engines. A continuous path from the surface of the stall edge may thereby be provided, ensuring adequate cooling thereof.
    The present disclosure is directed, at least in part, to improving and overcoming one or more aspects of the prior systems.
    Summary of the Revelation
    In one aspect, the present disclosure is directed to a piston of an internal combustion engine. The piston may have a piston skirt with a central axis M and a piston at the top with a diameter D which bounds the piston skirt at the top. The piston head may be formed by a piston bottom edge with a width b and a piston trough with a depth t. The piston recess may be formed as a pot well and a piston recess bottom and a piston bowl wall with a diameter d4, which adjoins have. The piston bowl 2.2 may have an opening cross section A, which is aligned symmetrically relative to the central axis M and has a diameter da, which may be smaller than the diameter d4. As a result of the reduced diameter dA, a stall edge, which is designed as a nose, may be formed in the region of the opening cross-section A. The nose may protrude inwardly radially beyond the piston bowl wall 4. A transition between the piston crown edge and the stall edge 5 may be formed by a radius Ro, and the stall edge may have a boundary zone g between the nose and the piston bowl wall having a radius Ru inside. A tangential transition may be provided between the radius Ro and the radius Ru.
    In another aspect, the present disclosure is directed to use of a piston for an Otto engine having, for example, external mixture formation. The piston used can have a piston skirt with a center axis M and a piston crown with a diameter D which delimits the piston skirt upwards. The piston head can be formed by a piston bottom edge with the width b. The piston bowl may be formed as a pot well, and it may have a piston bowl bottom and a piston bowl wall with a diameter d4, which adjoins. The piston bowl may have an opening cross section A symmetrically oriented relative to the center axis M and a diameter dA smaller than the diameter d4. And as a result of the reduced diameter dA, a stall edge formed as a nose may be formed in the area of the opening cross-section A. The nose may protrude inwardly radially beyond the piston bowl wall.
    Other features and aspects of this disclosure will become apparent from the following description and the accompanying drawings.
    Brief description of the drawing
    Further advantages and details of the invention are explained in the patent claims and in the description and illustrated in the figures. Show it:
    Figure 1 is a partial sectional view of the piston with piston recess;
    Figure 2 is a sectional view of an alternative embodiment;
    3 shows a schematic diagram of an engine block.
    Detailed description
    A piston 1 shown in FIG. 1 has a piston skirt 1.1 and a piston skirt 2 upwardly delimiting the piston skirt 2 with a piston diameter D, wherein the piston crown 2 is formed from a piston crown edge 2.1 and a piston skirt 2.2 which adjoins the piston crown edge 2.1 inwardly. Both the piston recess 2.2 and the piston bottom edge 2.1 are aligned coaxially to a central axis M of the piston 1.
    The piston bowl 2.2 has a depth t and an opening cross-section A with a diameter thereon. The piston bowl 2.2 or a piston bowl wall 4 has a somewhat larger diameter d4, so that, starting from the opening cross-section A, a circumferential flow-off edge 5 is formed.
    The piston recess 2.2 is thus formed from the stall edge 5, the piston bowl wall 4 adjoining the stall edge 5 and the piston bowl bottom 3 adjoining the piston bowl wall 4.
    The stall edge 5 has an upper radius Ro of 3 mm in the transition region to the piston crown edge 2.1. Downwardly, within a boundary zone g between the stall edge 5 and the piston bowl wall 4, the stall edge 5 is limited by a lower radius Ru of about 10 mm.
    The piston bowl wall 4 is inclined with respect to the central axis M by an angle α of about 5 degrees. The piston bowl wall 4 or its diameter d4, starting from the opening cross-section A, increases continuously towards the bottom and has at the lower end of said diameter d4.
    The ratio of Ro to D is about 0.02. The ratio of Ru to D is about 0.1. The ratio of da to d4 is about 0.9.
    According to the embodiment of Fig. 2, the adjustment of the piston bowl wall 4 is positive, i. the piston bowl wall 4 or its diameter d4 tapers, starting from the opening cross-section A. The angle α between the piston bowl wall 4 and the central axis M is also substantially larger and is about 15 degrees.
    By forming the above-described stall-edge 5 a width b of the piston edge 2.1 is slightly larger than in the case of non-existence of such a stall-edge 5. This in turn establishes a slightly increased squish flow between the area above the piston crown edge 2.1 and the piston bowl 2.2 in the up and down movement of the piston 1 in the cylinder. The squish flow is slightly influenced by valve pockets 2.3, 2.3 'in the piston bottom edge 2.1 according to the embodiment of FIG.
    Fig. 3 shows in principle an engine block 6 with a plurality of pistons 1, 1 'contained therein according to one of the embodiments of FIGS. 1 and 2.
    Industrial Applicability
    A piston according to the present disclosure may be provided with a specific piston crown for an engine so that improved combustion can be achieved. In particular, in the case of a gasoline engine or a gasoline engine, an early ignition due to a hot stall edge and accordingly a knocking of the engine can be prevented.
    At the trailing edge of the present piston results in a defined stall, which can increase the turbulence in the rotating chamber. The increased turbulence leads to accelerated combustion and faster and better burnout in the piston bowl. This increases the efficiency and the knocking distance of the engine. In addition, with the formation of the spoiler lip, an enlarged diameter dm of the piston bowl is accompanied by a constant width b of the piston crown edge, so that the depth t of the piston bowl can be reduced with a constant volume of the piston bowl. The diameter D of the piston head corresponds to the piston diameter. The piston diameter may also correspond to the diameter da of the opening cross section A of the piston recess plus twice the width b of the piston bottom edge.
    The ratio of the diameter da of the opening cross-section A to the diameter D of the piston crown and the piston diameter, respectively, according to an embodiment of the present disclosure satisfies the following condition: d / D = 0.4 - 0.6.
    According to another embodiment of the present disclosure, the ratio of the depth t of the piston bowl to the diameter D of the piston head and the piston diameter, respectively, satisfies the following condition: t / D = 0.15 - 0.35.
    According to a further embodiment of the present disclosure, the piston recess may have a symmetrical or coaxial with the central axis M aligned opening cross-section A with a diameter da, which is smaller than the diameter d4 and for which by the reduced diameter da nose formed as a stall edge in the Opening cross section A is formed, wherein the nose protrudes in the radial direction over the piston bowl wall inwardly for an Otto engine with external mixture formation. In the prior art, the stall edge was provided to enhance the mixing of the injected diesel with the combustion air. In the case of a gas engine with external mixture formation, this mixing of fuel and combustion air is no longer necessary. A stall edge, as described in the prior art for diesel engines, so is not necessary for a gas engine with external mixture formation.
    When using such a piston for a gas engine with external mixture formation, it may also be advantageous if a transition between the piston crown edge and the stall edge is formed by a radius Ro and the stall edge within a boundary zone g between the nose and the piston bowl wall has a radius Ru, wherein between the radius Ro and the radius Ru, a tangential transition is provided.
    It may be advantageous in the engine, as well as in use, when the piston bowl wall with the center axis M win-kel cz includes, wherein the angle α over at least 50% of the depth t of the piston recess a) for a flared to the piston bowl bottom piston recess no larger is 4 ° to 7 °, or b) is not smaller than 13 ° to 11 ° for a piston recess tapering towards the piston bowl bottom (3). The piston bowl is pot-like, i. designed with a relatively steep piston bowl wall, so that although the desired turbulence can be achieved. A Tumbleströmung, as it is favored by flat piston recesses, but should just be counteracted. In addition, no flatter employment of Kolbenmuldenwand due to a Kraftstoffstrahleinspritzrichtung is necessary because the piston is designed for an Otto engine with external mixture formation.
    Further, it may be advantageous if the ratio of the radius Ru to the diameter D satisfies the following condition: W1 < = Ru / D < = W2, where 0.04 < = W1 < = 0.06 or Wl = 0.05 and 0.19 < = W2 < = 0.21 or W2 = 0.2. The radius Ru should not be too large for a defined stall. The radius Ru should also not be too small, so that the stall edge does not get too hot.
    It may also be advantageous if, in the region of the piston bowl wall, between 3 mm to 10 mm or between 0.02 D and 0.05 D below the radius, since the diameter d4 is larger by a dimension M1 than the diameter da, with 2 mm < = Ml < 6 mm and 0.01 D < = Ml < = 0.05 D. This, in turn, provides a sufficiently large flow deflection gradient to introduce a sufficient level of turbulence.
    Also of importance to the present invention is when the ratio of the radius Ro to the diameter D satisfies the following condition: W3 <= Ro / D <= W4, with 0.005 <= W3 <= 0.015 or W3 = 0.01 and 0.02 &lt; = W4 &lt; = 0.04 or W4 = 0, 03. The
    Radius Ro should adequately support the squish flow that changes between the piston bowl and the piston crown.
    The Radius Ro should not be too large for a defined stall. Also, the Radius Ro should not be too small so that the stall edge does not get too hot.
    In connection with the design and arrangement according to the invention, it may be advantageous if the ratio of the diameter da to the diameter d4 satisfies the following condition: W5 <= da / d4 <= W6, with 0.7 <= W5 &lt; = 0.9 or W5 = 0.8 and 0.9 <= W6 <= 1.0 or W6 = 0.98.
    The taper of the opening of the piston bowl should be sufficiently large to ensure a sufficiently large gradient for the flow deflection.
    The object is also achieved by an engine block of an Otto engine with internal or external mixture formation with a piston guided therein, as described above. The knocking of the petrol engine is prevented by avoiding too hot a stall edge.
    权利要求:
    Claims (15)
    [1]
    1. Piston (1) of an internal combustion engine with a central axis M having a piston skirt (1.1) and the piston skirt (1.1) upwardly bounding piston head (2) with a diameter D, wherein the piston head (2) is formed from a piston crown edge ( 2.1) of the width b and a piston recess (2.2) with a depth t, wherein the piston recess (2.2) is formed as Topfmulde and a Kolbenmuldenboden (3) and an adjoining Kolbenmuldenwand (4) having a diameter d4; the piston recess (2.2) has an opening cross section A which is symmetrical to the central axis M and has a diameter da smaller than the diameter d4; in that the nose (5) protrudes inward in the radial direction via the piston bowl wall (4), and wherein a transition between the piston crown edge (5) is formed by the reduced diameter since a stall edge (5) formed as a nose in the region of the opening 2.1) and the stall edge (5) is formed by a radius Ro and the stall edge (5) within a boundary zone g between the nose (5) and the piston bowl wall (4) has a radius Ru, wherein between the radius Ro and the radius Ru a tangential transition is provided.
    [2]
    2. Piston (1) according to claim 1, wherein the piston bowl wall (4) with the central axis M forms an angle α, wherein the angle α over at least 50% of the depth t of the piston recess (2.2) a) for a piston bowl bottom (3 ) widening piston recess (2.2) is not greater than 4 ° to 7 ° or b) for a to the piston bowl bottom (3) towards tapered piston bowl (2.2) is not less than 13 ° to 17 °.
    [3]
    The piston (1) according to claim 1 or 2, wherein the ratio of the radius Ru to the diameter D satisfies the following condition: W1 &lt; = Ru / D &lt; = W2, where 0.04 &lt; = W1 &lt; = 0.06 or W1 = 0.05 and 0.19 <= W2 <= 0.21 or W2 = 0.2.
    [4]
    4. Piston (1) according to one of the preceding claims, wherein in the region of the piston bowl wall (4) between 0.02 D and 0.05 D below the radius since the diameter d4 by a measure Ml is greater than the diameter there, with 0th , 01 D <= Ml <= 0.05 D.
    [5]
    A piston (1) according to any one of the preceding claims, wherein the ratio of the radius Ro to the diameter D satisfies the following condition: W3 <= Ro / D <= W4, with 0.005 <= W3 <= 0.015 or W3 = 0.01 and 0.02 &lt; = W4 &lt; = 0.04 or W4 = 0.03.
    [6]
    A piston (1) according to any one of the preceding claims, wherein the ratio of the diameter da to the diameter d4 satisfies the following condition: W5 <= da / d4 <= W6, with 0.7 <= W5 <= 0.9 or W5 = 0.8 and 0.9 <= W6 <= 1.0 or W6 = 0.98.
    [7]
    7. gasoline engine (6) with internal or external mixture formation with a guided therein piston (1) according to one of the preceding claims.
    [8]
    8. Use of a piston (1) for an Otto engine (6) with external mixture formation, wherein the piston has a central axis M having a piston skirt (1.1) and a piston skirt (1.1) upwardly bounding piston head (2) with a diameter D. has, wherein the piston head (2) is formed of a piston bottom edge (2.1) of the width b and a piston recess (2.2) with a depth t, wherein the piston recess (2.2) is designed as Topfmulde and a Kolbenmuldenboden (3) and an adjacent thereto Piston well wall (4) having a diameter d4, and the piston recess (2.2) has a symmetrical to the central axis M aligned opening cross-section A with a diameter da, which is smaller than the diameter d4, and by the reduced diameter da nose formed as a stall Edge (5) is formed in the region of the opening cross section A, wherein the nose (5) in the radial direction on the piston bowl wall (4) projects inwardly.
    [9]
    9. Use according to claim 8, wherein a transition between the piston crown edge (2.1) and the stall edge (5) is formed by a radius Ro and the stall edge (5) within a boundary zone g between the nose (5) and the Piston well wall (4) has a radius Ru, wherein between the radius Ro and the radius Ru, a tangential transition is provided.
    [10]
    10. Use according to claim 8 or 9, wherein the piston bowl wall (4) with the center axis M at an angle α over at least 50% of the depth t of the piston recess (2.2) c) for a piston depression bottom (3) flared piston recess (2.2) is not greater than 4 ° to 7 °, or d) is not smaller than 13 ° to 17 ° for a piston recess (2.2) tapering towards the piston bowl bottom (3).
    [11]
    Use according to claim 8, 9 or 10, wherein the ratio of the radius Ru to the diameter D satisfies the following conditions: W1 <= Ru / D <= W2, with 0.04 <= W1 <= 0 , 06 or W1 = 0.05 and 0.19 <= W2 <= 0.21 or W2 = 0.2.
    [12]
    Use according to claim 8, 9 or 10, wherein the ratio of the radius Ru to the diameter D satisfies the following conditions: W1 &lt; = Ru / D &lt; = W2, with 0.04 &lt; = W1 &lt; = 0 , 06 or W1 = 0.05 and 0.19 <= W2 <= 0.21 or W2 = 0.2.
    [13]
    13. Use according to one of claims 8 to 12, wherein in the region of the piston bowl wall (4) between 0.02 D and 0.05 D below the radius because the diameter d4 is greater than the diameter da by da, with 0, 01 D <= Ml <= 0.05 D.
    [14]
    Use according to any one of claims 8 to 13, wherein the ratio of the radius Ro to the diameter D satisfies the following condition: W3 <= Ro / D <= W4, with 0.005 <= W3 <= 0.015 or W3 = 0.01 and 0.02 &lt; = W4 &lt; = 0.04 or W4 = 0.03.
    [15]
    Use according to any one of claims 8 to 14, wherein the ratio on the diameter da to the diameter d4 satisfies the following condition: W5 <= da / d4 <= W6, with 0.7 <= W5 <= 0 , 9 or W5 = 0.8 and 0.9 <= W6 <= 1.0 or W6 = 0.98.
    类似技术:
    公开号 | 公开日 | 专利标题
    DE102012103206B4|2017-08-03|Piston of an internal combustion engine
    AT514637B1|2016-03-15|Piston of an internal combustion engine
    DE102012103212A1|2013-10-17|Piston of an internal combustion engine
    DE10303721B4|2009-09-03|Engine with spark ignition with flat piston bowl geometry
    DE2234561A1|1973-01-25|DIESEL ENGINE WITH FUEL INJECTOR AND COMBUSTION CHAMBER PROVIDED IN THE PISTON
    DE102005002389A1|2006-07-27|Vehicle piston internal combustion engine with adapted trough
    DE102008025687A1|2009-07-30|Piston for internal combustion engines with squish-induced, mixture-enhanced low emissions
    AT514638A2|2015-02-15|Piston of an internal combustion engine
    DE102015016920B4|2021-03-18|Combustion chamber structure for an engine and internal combustion engine
    DE102015012541A1|2016-04-14|Piston for a gas engine and gas engine with such a piston
    DE60319166T2|2009-03-12|Method and internal combustion engine for secure mixture of at least one gaseous fluid, such as air, and a fuel in a combustion chamber of a direct-injection internal combustion engine
    DE2913763C2|1983-12-01|Reciprocating internal combustion engine
    DE3245780C1|1983-12-29|Externally ignited, air compressing internal combustion engine
    EP2489848B1|2017-11-01|Gas petrol engine
    DE102016102582A1|2016-08-18|PISTON FLOOR FOR INCREASING THE COMPACTION RATIO
    DE102015004357A1|2016-10-06|Piston crown for internal combustion engines
    DE102014002625A1|2015-08-27|Piston for a reciprocating internal combustion engine and cylinder head for a reciprocating internal combustion engine
    DE3612029A1|1986-11-06|AIR COMPRESSING PISTON COMBUSTION ENGINE
    DE19962293A1|2001-06-28|Piston internal combustion engine has direct fuel injection, roof-shaped cylinder ceiling and piston base in vertical section, one roof surface associated with inlet valves, one with outlet valve
    EP3486447A1|2019-05-22|Piston, in particular for a hpdi-diesel gas combustion engine
    DE102015202361A1|2016-08-11|Reciprocating internal combustion engine
    WO2015154853A1|2015-10-15|Piston for an internal combustion engine
    EP2401489B1|2012-07-25|Otto motor comprising a piston having a depression
    DE202016008281U1|2017-06-20|Cylinder for increasing the displacement of an internal combustion engine
    DD207399A1|1984-02-29|AIR COMPRESSIVE, DIRECT INJECTIVE INTERNAL COMBUSTION ENGINE
    同族专利:
    公开号 | 公开日
    DE102012103193B4|2018-05-30|
    US20150068487A1|2015-03-12|
    WO2013152871A1|2013-10-17|
    CN104428508A|2015-03-18|
    DE102012103193A1|2013-10-17|
    AT514638A5|2015-05-15|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    JPS5297009A|1976-02-09|1977-08-15|Riyuuzou Tsukamoto|Internal combustion engine|
    GB1540457A|1976-09-23|1979-02-14|Lister & Co Ltd R|Piston for an internal combustion engine|
    DE2828237C3|1978-06-28|1983-03-24|Klöckner-Humboldt-Deutz AG, 5000 Köln|Air-compressing reciprocating internal combustion engine|
    DE3115933C2|1981-04-22|1986-10-23|Daimler-Benz Ag, 7000 Stuttgart|Self-igniting internal combustion engine with a rotationally symmetrical piston bowl|
    JPS5910734A|1982-07-09|1984-01-20|Toyota Central Res & Dev Lab Inc|Compression-ignition type direct-injecting internal-combustion engine|
    DE3302427C2|1983-01-26|1985-01-24|Daimler-Benz Ag, 7000 Stuttgart|Self-igniting internal combustion engine with a rotationally symmetrical piston bowl|
    DE3590066C2|1984-02-15|1993-06-24|Mitsubishi Jidosha Kogyo K.K., Tokio/Tokyo, Jp|
    JPS62113822A|1985-11-12|1987-05-25|Nippon Clean Engine Res|Combustion system for internal combustion engine|
    JPS631710A|1986-06-19|1988-01-06|Nippon Clean Engine Lab Co Ltd|Spark ignition fuel injection stratified charge combustion system and various fuels high-compression stratified combustion engine|
    DE3632579C2|1986-09-25|1990-07-12|Man Nutzfahrzeuge Ag, 8000 Muenchen, De|
    JPH031710A|1989-05-30|1991-01-08|Kinseki Ltd|Piezoelectric vibration|
    JPH0417716A|1990-05-09|1992-01-22|Hino Motors Ltd|Fuel injector|
    US5329902A|1991-02-02|1994-07-19|Sanshin Kogyo Kabushiki Kaisha|Cylinder fuel injection type two-cycle internal combustion engine|
    JP3315484B2|1993-07-07|2002-08-19|正 村山|Diesel engine|
    JPH0996241A|1995-10-02|1997-04-08|Mitsubishi Motors Corp|Combustion device for diesel engine|
    JPH112128A|1997-06-13|1999-01-06|Nippon Soken Inc|Direct injection type engine|
    AT3135U1|1998-06-18|1999-10-25|Avl List Gmbh|METHOD FOR OPERATING AN INTERNAL COMBUSTION ENGINE OPERATING WITH ANY ALTERNATIVE, OR ALSO AUTO, IGNITION|
    JP2001227346A|2000-02-18|2001-08-24|Honda Motor Co Ltd|Fuel direct infection-type diesel engine|
    WO2002088528A1|2001-04-27|2002-11-07|General Motors Corporation|Low emission fuel efficient diesel locomotive engine including a piston having a toroidal surface|
    US6745745B2|2002-02-22|2004-06-08|General Motors Corporation|Combustion chamber for reverse tumble spark ignition direct injection engine|
    US6705273B1|2002-09-30|2004-03-16|International Engine Intellectual Property Company, Llc|Combustion chamber|
    US6971365B1|2004-07-12|2005-12-06|General Motors Corporation|Auto-ignition gasoline engine combustion chamber and method|
    US20100108044A1|2008-11-06|2010-05-06|International Engine Intellectual Property Company, Llc|Combustion Chamber with Double Convex Surfaces and Double Concave Surfaces|
    US8683974B2|2011-08-29|2014-04-01|Electro-Motive Diesel, Inc.|Piston|US20160169152A1|2014-12-11|2016-06-16|Caterpillar Inc.|Engine Piston|
    US10400663B2|2017-12-18|2019-09-03|Caterpillar Inc.|Piston bowl for improved combustion stability|
    DE102018102248A1|2018-02-01|2019-08-01|Man Truck & Bus Ag|Method for operating an Otto gas engine|
    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:
    2019-07-15| REJ| Rejection|Effective date: 20190715 |
    优先权:
    申请号 | 申请日 | 专利标题
    DE102012103193.2A|DE102012103193B4|2012-04-13|2012-04-13|Use of a piston for an Otto engine with external mixture formation and gasoline engine|
    [返回顶部]