• 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 having 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. The Kol benboden (2) formed from a piston bottom edge (2.1) of a width b and a piston bottom trough (2.2) with a depth t. The piston crown (2.2) may have a piston bowl wall (2.2a) with egg nem opening cross section with a diameter (d). In within the piston bottom edge (2.1) can at least one circumferentially U to the central axis M extending groove (3) provided with egg nem inner diameter dn and the inner diameter dn be greater than the diameter d.
    公开号:AT514637A2
    申请号:T9149/2013
    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 such as a gasoline engine with external mixture formation, in particular the invention relates to a piston which may have a piston skirt having a center axis M and a piston skirt having a diameter D bounding the piston skirt upwardly. The piston head can be formed from a piston bottom edge of a width b and a piston bottom recess with a depth t. Furthermore, the piston crown can have a piston bowl wall with an opening cross-section with a diameter d. The invention further relates to a diesel engine or gasoline engine or Otto gas engine with a piston guided therein. In particular, the piston guided therein may be of the type previously described. The gasoline engine or gasoline engine may be an engine with external or internal mixture formation.
    background
    From DE 10 2010 018 930 Al a piston for an internal combustion engine is known, which has four valve pockets within the piston head, which ensures a clearance of the exhaust and intake valves.
    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 bottom. The piston head is designed for diesel operation for optimal direct injection and is used unchanged for cost reasons and for simplicity h in the gas Otto engine. The latter, however, regardless of a possibly worse combustion process. D) Piston with pot-piston bottom tray. 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 ducts and chamber candles pistons with pot-piston bottom wells are very well suited. During the compression stroke, the mixture is displaced above the piston bottom edge (squish edge) of the piston into the pot piston bottom recess. During the expansion stroke, the mixture is sucked out of the pot bottom of the piston. This process leads to strong squish currents (squish flows), especially near top dead center.
    In addition to the squish flow, the pot bottom of the pot 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 bottom of the pot bottom.
    The object of the invention is to design and arrange a piston crown for an engine such that improved combustion is ensured.
    Summary of the Revelation
    According to one aspect of the present disclosure, a piston for an internal combustion engine may include a piston skirt having a center axis M and a piston skirt having a diameter D upwardly bounding the piston skirt. The piston head may be formed by an edge of the piston head having a width b and a piston bottom trough having a depth t. The piston crown can have a piston bowl wall with an opening cross-section with a diameter d. At least one groove with an inner diameter dn can be provided within the piston bottom edge and extend in the circumferential direction U relative to the central axis M. The inner diameter dn may be greater than the diameter d of the opening cross section of the piston crown.
    In accordance with another aspect of the present disclosure, a diesel engine or gasoline engine or gasoline engine may include at least one piston carried therein. The piston may be formed as described above.
    Brief description of the drawings
    Further advantages and details of the invention are explained in the claims and in the description and illustrated in the figures. In the figures show
    Figure 1 is a perspective view of a piston;
    Figure 2a-2c different basic shapes of a groove;
    Figure 3 is a sectional view of the piston with trough;
    Figure 4 shows a motor with multiple pistons.
    Detailed description
    A piston 1 shown in FIG. 1 is formed from a piston skirt 1.1 with a central axis M and a diameter D and a piston skirt 2 bounding the piston skirt 1.1 upwards with correspondingly equal diameter D. The piston crown 2 itself is formed from a piston crown edge 2.1 of the width b and a coaxial with a central axis M of the piston 1 arranged piston bottom trough 2.2. The piston bottom trough 2.2 has an opening cross section. This corresponds approximately to a maximum inner diameter dn, because the piston crown is 2.2 formed almost cylindrical. The piston bowl 2.2 has a depth T and is bounded at the bottom by a piston bowl bottom 5 and a piston bowl wall 4 adjoining the piston bowl bottom 5.
    Within the piston bottom edge 2.1 a circumferential groove 3 is provided with a radius R of about 2 mm. The groove 3 has an inner diameter dn which is about 15% larger than the diameter d of the opening cross section of the piston recess 2.2. The groove 3 has in the transition region to the piston bottom edge 2.1 a radius RI, R2, wherein the inner radius RI is about 2.5 mm and the outer radius R2 is about 2 mm.
    According to Fig. 2A, two grooves 3, 3 'are provided. Each groove 3, 3 'has a circular basic shape G, G' and is, as shown in FIG. 1, arranged with respect to an axis of symmetry S of the groove 3, 3 'coaxial with the central axis M.
    According to the embodiment of Fig. 2b, the groove 3 has an oval basic shape G and it is arranged symmetrically to the central axis M. The two symmetry axes S, S 'of the groove 3 are arranged eccentrically to the central axis M.
    According to the embodiment of FIG. 3, left half of the part, the groove 3 has a height h of about 12% of the depth t of the piston bowl 2.2. Furthermore, the groove 3 has a radial extent r of about 20% of the width b of the piston bottom edge 2.1.
    According to the embodiment of FIG. 3, right half of the image, two grooves 3, 3 'are provided within the piston bottom edge 2.1. Both grooves are arranged in relation to a symmetry axis S of the respective groove 3, 3 'coaxial with the central axis M.
    Within the piston 1, a cooling channel 7 is also provided, which is also arranged coaxially to the central axis M.
    4, an engine 6 six pistons 1, 1 'of the type described above.
    Industrial Applicability
    A piston according to the present disclosure and as described herein may be configured to achieve improved combustion. In particular, the generation of the squish flow and the amplification of the swirl flow have a positive effect on the combustion. Due to the disclosed piston, it could be possible to purposefully convert these directed flows into turbulence. This could further improve combustion.
    In one embodiment of the present disclosure, the inner diameter may satisfy the following requirement: dn> = 1.1 d, that is, at least 10% larger than the diameter d, which is the diameter of the opening cross-section. Due to the at least one groove with the inner diameter dn, which can be referred to as turbulence rotation, the squish flow prevailing above the piston bottom edge can be broken and a turbulent flow fraction can be established. The turbulent flow rate is likely to optimize combustion. The Squish flow may be broken by the groove or grooves on the piston crown edge in a direction perpendicular to the Squish flow and converted into turbulence.
    In a further exemplary embodiment of the present disclosure, the at least one turbulence groove can be positioned, for example, in the vicinity of the piston bottom recess, in the middle of the piston bottom edge and / or on the outer diameter in the region of the piston skirt or the cylinder wall.
    The latter can additionally lead to a lowering of the plank dead space volume. In this case, an outer diameter of the groove may correspond to the diameter D of the piston.
    In another embodiment of the present disclosure, it would also be possible to displace the groove to the inside of the piston crown edge toward the piston bowl wall so that the inner diameter dn would be as large as the diameter d of the opening cross section of the piston bowl. The effect achievable would be equal to an enlarged piston recess and would perhaps be negligible.
    In a further embodiment of the present invention, the groove may have a radius RI, R2 in the transition region to the piston bottom edge, wherein both the inner radius RI and the outer radius R2 may be between 1 mm and 5 mm, preferably 2 mm to 3 mm. The radii must not be too small so that the edges do not get too hot. The radii must not be too large, since the discontinuity of the geometry and thus the achievable turbulence entry can be reduced. The measure described above can increase the turbulence in the combustion chamber. The increased turbulence can lead to accelerated combustion and faster and better burnout in the cylinder. This could increase the efficiency and knocking distance of the engine. In this embodiment of the present disclosure, the diameter D of the piston crown may correspond to the piston diameter. The diameter d of the opening cross section of the piston crown plus twice the width b of the piston crown edge can give the piston diameter d. The ratio d / D of the diameter d of the opening cross-section or the bowl diameter to the diameter D of the piston head or the piston diameter is between 0.4 and 0.6. The ratio t / D of the depth t of the piston crown to the diameter D of the piston head or the piston diameter may be between 0.15 and 0.35.
    In another embodiment of the present disclosure, it may also be advantageous for this purpose if the groove has a radial extent r with respect to the center axis M and has 1 mm <= r <= 0.5 b or 2 mm <= r <1. = 0.4b. The turbulence effect can be dependent on the radial extent r of the groove. For the radial expansion r, a minimum dimension of approx. 1 mm to 2 mm must be assumed, so that the achievable turbulence entry is effective. The smaller the radial extent r, the more grooves can be provided on the piston bottom edge.
    In addition, according to another embodiment of the present disclosure, when the groove has a height h with respect to the axial direction of the center axis M, it may be advantageous to have 1mm <= h <= 0.2t or 2mm <= h <1 = 0.1 t. The same applies to the height h of the groove. The height h of the groove should not be less than a minimum of about 1 mm to 2 mm, so that the achievable turbulence effect is effective.
    In another exemplary embodiment of the present disclosure, it can also be advantageous if two, three, four, or more grooves are provided distributed over the width b of the piston bottom edge. With the formation of several grooves of the turbulence entry can be strengthened. Which combination of the parameters radial expansion r, height h and number ensures the largest turbulence entry can be dependent on the respective combustion chamber conditions.
    In addition, according to still another embodiment of the present disclosure, when the groove extends over the entire circumference U, it may be advantageous. Symmetrical space conditions may sometimes be advantageous, and deviations may also be provided. The extent of the groove in the circumferential direction U can be adapted to the current flow conditions present. The groove may extend over the entire circumference U or may be provided only in the form of sub-segments over part of the circumference U, the latter in particular in the region of the intake valves.
    Furthermore, according to a further exemplary embodiment of the present disclosure, it can be advantageous if the groove has an axis of symmetry S which is arranged coaxially or eccentrically to the central axis M. Symmetrical space ratios are sometimes advantageous, and deviations may also be provided, such as. in the case of an oval piston recess with eccentric to the central axis M arranged symmetry axes S, S '. With an eccentric arrangement, different flow conditions can be ensured for the areas of the intake and exhaust valves.
    In addition, in another embodiment of the present disclosure, it may be advantageous if the groove has a basic geometry G, wherein the basic geometry G is formed circular or oval. With the deviation from the circular shape, despite the symmetrical arrangement of the groove to the central axis M different flow conditions can be ensured over the circumference.
    In yet another embodiment of the present disclosure, it may be advantageous if at least two grooves are provided, wherein the grooves have the same or different basic shapes G, G '. A combination of different groove geometries ensures optimal adaptation to the given installation space and flow conditions.
    权利要求:
    Claims (10)
    [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 a width b and a piston bottomed trough (2.2) with a depth t, wherein the piston bottomed trough (2.2) has a piston bowl wall (2.2a) with an opening cross section with a diameter d, wherein within the piston bottom edge (2.1) at least one in the circumferential direction U to Central axis M extending groove (3) is provided with an inner diameter dn, wherein the inner diameter dn is greater than the diameter d of the opening cross-section of the piston crown (2.2).
    [2]
    A piston (1) according to claim 1, wherein the groove (3) has a radial extent r with respect to the center axis M and is 1mm &lt; = r &lt; 0.5 b.
    [3]
    A piston (1) according to claim 1 or 2, wherein the groove (3) has a height h with respect to the axial direction of the center axis M, with 1 mm &lt; = h &lt; = 0.2 t.
    [4]
    4. piston (1) according to any one of the preceding claims, wherein distributed over the width b of the piston bottom edge (2.1) two, three, four or grooves (3,3 ') are provided.
    [5]
    5. piston (l) according to any one of the preceding claims, wherein the groove (3) over the entire circumference U extends.
    [6]
    6. piston (1) according to any one of the preceding claims, wherein the groove (3) has an axis of symmetry S, which is arranged coaxially or eccentrically to the central axis M.
    [7]
    7. piston (1) according to any one of the preceding claims, wherein the groove (3) has a basic geometry G, which is circular.
    [8]
    8. piston (1) according to one of claims 1 to 4, wherein the groove (3) has a basic geometry G, which is formed oval.
    [9]
    9. piston (1) according to any one of claims 7 or 8, wherein at least two grooves (3, 3 ') are provided, wherein the grooves have the same or different basic shapes (G, G').
    [10]
    10. Diesel engine (6) or gasoline engine (6) or Otto gas engine (6) with a piston guided therein (1) according to one of the preceding claims.
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    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    CH183532A|1935-02-09|1936-04-15|Buechi Alfred|Valve-controlled four-stroke internal combustion engine.|
    FR801538A|1935-02-09|1936-08-06|Four-stroke controlled valve internal combustion engine|
    GB522313A|1938-12-08|1940-06-14|Crossley Motors Ltd|Improvements relating to compression ignition type oil engines|
    US2172170A|1939-06-17|1939-09-05|Megroot John Peter|Internal combustion engine|
    GB546500A|1941-03-12|1942-07-16|Gardner & Sons Ltd|Improvements in and relating to the combustion chambers of compression ignition oil engines|
    DE1526289A1|1966-10-11|1970-04-02|Daimler Benz Ag|Piston internal combustion engine with fuel injection|
    US3508531A|1968-05-31|1970-04-28|Int Harvester Co|Arrangement of cylinder and piston in engine|
    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|
    JPS5949407B2|1976-11-15|1984-12-03|Toyota Motor Co Ltd|
    US4114518A|1977-04-07|1978-09-19|Caterpillar Tractor Co.|Piston valve pocket relief|
    DE2828237C3|1978-06-28|1983-03-24|Klöckner-Humboldt-Deutz AG, 5000 Köln|Air-compressing reciprocating internal combustion engine|
    DE2945490A1|1978-11-16|1980-05-22|List Hans|AIR COMPRESSING, DIRECTLY INJECTING INTERNAL COMBUSTION ENGINE|
    FR2451458B2|1979-03-15|1983-05-27|Peugeot|
    GB2074231A|1980-04-01|1981-10-28|Coates B F|Improvements in or relating to reciprocating internal combustion engines|
    US4440125A|1981-05-18|1984-04-03|General Motors Corporation|Diesel engine combustion chamber|
    JPS5910734A|1982-07-09|1984-01-20|Toyota Central Res & Dev Lab Inc|Compression-ignition type direct-injecting internal-combustion engine|
    JPS59158317A|1983-02-28|1984-09-07|Hino Motors Ltd|Piston|
    GB8317453D0|1983-06-28|1983-08-03|Massey Ferguson Perkins Ltd|Ic engine|
    DE3590066C2|1984-02-15|1993-06-24|Mitsubishi Jidosha Kogyo K.K., Tokio/Tokyo, Jp|
    US4635597A|1985-01-16|1987-01-13|Yanmar Diesel Engine Co., Ltd.|Structure of a main combustion chamber of a diesel engine of a direct injection type|
    IT8548542D0|1985-09-10|1985-09-10|Cola Umberto|DEVICE TO INCREASE THE POWER, SPEED AND PERFORMANCE OF THE COMBUSTION ENGINE AND THE DIESEL ENGINE|
    JP2778685B2|1985-09-27|1998-07-23|三菱重工業株式会社|Combustion device for diesel engine|
    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|
    EP0352549B1|1988-07-29|1995-06-07|Siemens Aktiengesellschaft|Carry select adder|
    US5065715A|1990-02-07|1991-11-19|The University Of British Columbia|Squish jet combustion chamber|
    US5103784A|1990-02-07|1992-04-14|The Univeristy Of British Columbia|Squish jet combustion chamber|
    US5329902A|1991-02-02|1994-07-19|Sanshin Kogyo Kabushiki Kaisha|Cylinder fuel injection type two-cycle internal combustion engine|
    US5285755A|1993-03-08|1994-02-15|Chrysler Corporation|Open chamber diesel engine having a piston with recesses therein|
    JP3315484B2|1993-07-07|2002-08-19|正 村山|Diesel engine|
    DE4415073A1|1994-04-29|1995-11-02|Fev Motorentech Gmbh & Co Kg|IC engine using alcohol-based fuel with spark ignition and direct fuel injection|
    DE29515308U1|1995-09-25|1996-01-04|Lipa Peter|Pistons for internal combustion engines, preferably with direct injection, with radial relief notches around the combustion chamber bowl|
    JPH0996241A|1995-10-02|1997-04-08|Mitsubishi Motors Corp|Combustion device for diesel engine|
    JPH09228838A|1996-02-26|1997-09-02|Shin A C Ii:Kk|Direct injection type diesel engine|
    JPH1193779A|1997-09-26|1999-04-06|Kubota Corp|Cylinder injection type gas 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|
    DE19829384A1|1998-07-01|2000-01-05|Man Nutzfahrzeuge Ag|Piston for a diesel internal combustion engine|
    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|
    US6708666B2|2001-10-10|2004-03-23|Southwest Research Institute|Multi-zone combustion chamber for combustion rate shaping and emissions control in premixed-charge combustion engines|
    SE524347C2|2002-02-01|2004-07-27|Scania Cv Abp|Internal combustion engine|
    US6745745B2|2002-02-22|2004-06-08|General Motors Corporation|Combustion chamber for reverse tumble spark ignition direct injection engine|
    US7210448B2|2002-06-11|2007-05-01|Cummins, Inc.|Internal combustion engine producing low emissions|
    US6705273B1|2002-09-30|2004-03-16|International Engine Intellectual Property Company, Llc|Combustion chamber|
    DE10261185A1|2002-12-20|2004-07-15|Daimlerchrysler Ag|Direct injection Otto internal combustion engine|
    JP4384945B2|2004-07-09|2009-12-16|ヤンマー株式会社|Combustion chamber shape of direct injection diesel engine|
    US6971365B1|2004-07-12|2005-12-06|General Motors Corporation|Auto-ignition gasoline engine combustion chamber and method|
    US7185614B2|2004-10-28|2007-03-06|Caterpillar Inc|Double bowl piston|
    DE102005002389B4|2005-01-19|2009-04-23|Fev Motorentechnik Gmbh|Vehicle piston internal combustion engine with adapted trough|
    FR2884284A1|2005-04-12|2006-10-13|Renault Sas|Piston for direct injection diesel engine, has piston head terminated by base in which bowl is made, reinforcement arranged at surface of boss in base of bowl, and another reinforcement made in base of head and outside bowl|
    FR2885958A1|2005-05-20|2006-11-24|Renault Sas|Piston for e.g. diesel engine, has combustion chamber divided into main and auxiliary chambers, where ratio between auxiliary chamber volume and total volume of main and auxiliary chamber volumes is between specified values|
    US7458358B2|2006-05-10|2008-12-02|Federal Mogul World Wide, Inc.|Thermal oxidation protective surface for steel pistons|
    FR2927121B1|2008-02-06|2010-02-12|Renault Sas|INTERNAL COMBUSTION ENGINE HAVING DOUBLE CAVITY COMBUSTION BOWL FOR ULTRASONIC INJECTOR|
    US20100108044A1|2008-11-06|2010-05-06|International Engine Intellectual Property Company, Llc|Combustion Chamber with Double Convex Surfaces and Double Concave Surfaces|
    JP2010112347A|2008-11-10|2010-05-20|Mitsubishi Fuso Truck & Bus Corp|Piston for direct injection type diesel internal combustion engine|
    JP2010156230A|2008-12-26|2010-07-15|Isuzu Motors Ltd|Engine piston|
    DE102009025063A1|2009-06-10|2010-12-30|Ks Kolbenschmidt Gmbh|Light metal piston with multiple omega combustion bowl|
    CN101705881A|2009-11-17|2010-05-12|哈尔滨工程大学|Rapid combustor of airflow hedging natural gas engine|
    US8459229B2|2010-04-20|2013-06-11|Southwest Research Institute|Piston bowl with spray jet targets|
    US9279361B2|2010-04-20|2016-03-08|Southwest Research Institute|Piston bowl with spray jet targets|
    DE102010018930A1|2010-04-30|2011-11-03|Daimler Ag|Piston for lifting cylinder machine, has front sided recess corresponding to outer contour of valve disk of valve of lifting cylinder machine, in which valve disk is accommodated|
    JP2012021429A|2010-07-13|2012-02-02|Daihatsu Motor Co Ltd|Internal combustion engine|
    DE102010027637A1|2010-07-19|2012-01-19|Mtu Friedrichshafen Gmbh|Piston for internal combustion engines, and internal combustion engine for this purpose|
    CN102182608A|2011-03-16|2011-09-14|奇瑞汽车股份有限公司|Combustion system of gasoline direct injection engine and control method thereof|
    US8683974B2|2011-08-29|2014-04-01|Electro-Motive Diesel, Inc.|Piston|DE102013022040A1|2013-12-20|2015-06-25|Daimler Ag|Piston for a reciprocating internal combustion engine|
    US9822977B1|2014-02-04|2017-11-21|Florida Turbine Technologies, Inc.|Advanced lean burn injector igniter system|
    US20160138518A1|2014-11-18|2016-05-19|Caterpillar Inc.|Engine Piston|
    FR3029984A3|2014-12-16|2016-06-17|Renault Sa|PISTON FOR INTERNAL COMBUSTION ENGINE|
    DE102015202361A1|2015-02-10|2016-08-11|Fev Gmbh|Reciprocating internal combustion engine|
    DE102016112538A1|2016-07-08|2018-01-11|Man Diesel & Turbo Se|Cylinder of an internal combustion engine and piston for such a cylinder|
    CN106014676A|2016-08-04|2016-10-12|广西玉柴机器股份有限公司|Piston of engine|
    CN106014677A|2016-08-04|2016-10-12|广西玉柴机器股份有限公司|Piston of engine|
    WO2018096592A1|2016-11-22|2018-05-31|マツダ株式会社|Diesel engine|
    法律状态:
    2018-12-15| MM01| Lapse because of not paying annual fees|Effective date: 20180412 |
    优先权:
    申请号 | 申请日 | 专利标题
    DE201210103195|DE102012103195A1|2012-04-13|2012-04-13|Piston of an internal combustion engine|
    PCT/EP2013/001075|WO2013152864A1|2012-04-13|2013-04-12|Piston of an internal combustion engine|
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