• 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) and an engine block (6) of an internal combustion engine with a guided therein piston (1) and with at least one guided therein, a central axis (6.3, 6.4) having gas exchange valve (6.1, 6.2). The piston (1) has a piston skirt (1.1) having a center axis M and a piston head (2) with a diameter (D) delimiting the piston skirt (1.1) upwardly. The piston head (2) is formed from egg nem piston bottom edge (2.1) and a piston bottomed trough (2.2) with egg ner a height (H) having piston bowl wall (3). At least one valve pocket (5.1), which has a minimum distance a to the gas exchange valve (6.1) when cold, ensures reliable clearance of the opened gas exchange valve (6.1), with 1 mm <a <2 mm. At least one valve pocket (5.1-5.4) is formed, at least partially, much deeper than is necessary for the clearance of the open gas exchange valve (6.3, 6.4). The distance a is increased at least in the area of the piston bowl wall (3) to a distance from A, with A> = + 2 mm.
    公开号:AT514635A2
    申请号:T9147/2013
    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. In particular, it relates to a piston having a piston skirt and a piston crown. The piston head can limit the piston skirt upwards. The piston head can be formed from a piston bottom edge and a piston bottom recess with a height H having piston bowl wall. At least one valve pocket can be embedded in the piston bottom edge, which has a depth T with respect to the piston bottom edge.
    The invention further relates to an engine block of an internal combustion engine, such as an Otto engine with external mixture formation. A piston and at least one gas exchange valve guided therein may be guided therein. The piston may have a piston skirt and a piston crown which delimits the piston skirt upwards. The piston head can be formed from a piston bottom edge and a piston bottom recess with a height H having piston bowl wall. At least one valve pocket can be embedded in the piston bottom edge, which has a minimum distance a to the gas exchange valve, which ensures safe clearance of the open gas exchange valve.
    background
    From DE 10 2010 018 930 Al, for example, a piston for an internal combustion engine is known, which has four valve pockets within the piston head, which guarantee a clearance of the exhaust and intake valves.
    In the Otto gas engine pistons are used with different Kolbenmuldenformen, as a rule, a distinction between the following conventional variants: A) piston with dachförmigem 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 crown is designed for diesel operation for optimal direct injection and is used for cost reasons and for simplicity, unchanged in the gas Otto engine. The latter regardless of a possibly worse combustion result. 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 pot-piston bottom tray. For engines with swirl inlet ducts and chamber candles pistons with pot-piston bottom wells are very well suited. During the Kopressionstaktes the mixture is displaced over the piston bottom edge (squish edge) of the piston in the pot-piston bottom mold. During the expansion stroke, the mixture is sucked out of the pot bottom of the piston. This process leads, especially near the top dead center, to strong pinch currents.
    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 present disclosure is directed, at least in part, to improving or 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 crown which bounds the piston skirt upwards.
    The piston head may have a diameter D and be formed by a piston bottom edge and a piston bottom trough having a wall height H. At least one valve pocket can be formed in the piston bottom edge. The at least one valve pocket may have a depth T with respect to the piston bottom edge, wherein the valve pocket depth T relative to the wall height H may bloom the following condition at least in the region of the piston bowl wall: in particular e.g.
    In another aspect, the present disclosure is directed to an engine block of an internal combustion engine. The engine block may have a piston guided in the engine block. The piston may have a piston skirt with a central axis M and a piston crown defining the piston skirt upwardly with a diameter D. The piston crown may be formed by a piston crown rim and a piston crown with a wall having a wall height H. At least one valve pocket can be formed in the piston bottom edge. At least one gas exchange valve may have a central axis and a minimum distance a from the piston bottom recess to ensure clearance of the opened gas exchange valve. At least one valve pocket is at least partially formed substantially deeper than necessary for the clearance of the open gas exchange valve.
    The distance a may be increased to a distance A at least in the region of the piston bottom wall, where A> = a + 2 mm.
    The minimum distance a can be increased to a distance A, at least in the region of the piston bowl wall, with A> = a + 2 mm, A> = a + 3 mm or A> = a + 4 mm or A> = a + 5 mm. The minimum distance A thus achieved is then at least 4 mm to 15 mm or 6 mm to 15 mm or 7 mm to 15 mm in the cold state. The latter at least in the area of the piston bowl wall.
    By deepening the valve pocket, the swirl flow prevailing in the region of the piston bowl wall is broken, so that a turbulent flow fraction is also established, which improves combustion. The valve pockets are designed significantly deeper than it would actually be required for the clearance of the valves. These designs can produce a strong refraction of the swirl flow with simultaneously low production costs. The measure described above can increase the turbulence in the combustion chamber. The increased turbulence leads to accelerated combustion and faster and better burnout in the cylinder. This may increase the efficiency and knocking distance of the engine.
    If no valve pockets are necessary for the actual operation of a piston, the effect according to the invention can of course also be achieved by attaching valve pockets. Such an embodiment is to be considered at least included in the range of equivalence of the claim.
    In the event that the minimum distance a is increased at least in the region of the piston bowl wall to the distance A, so that the desired turbulence entry is achieved, no valve pocket must be provided, whose diameter corresponds to the valve body. A recess in the piston bottom edge in the border region to the piston bowl wall is sufficient.
    The ratio H / D of the depth H of the piston crown to the diameter of the piston head or piston diameter D may be between 0.15-0.35 according to an embodiment of the present disclosure.
    It can also be advantageous for this purpose if the valve pocket has a valve pocket bottom with a surface normal N, wherein the surface normal N of at least one valve pocket is arranged at an angle β inclined to the center axis M, with 1 ° ≦ β ≦ 25 ° or 5 ° &lt; = β &lt; = 20 ° or 5 ° &lt; = β &lt; = 10 °, wherein the depth T increases toward the bottom of the piston crown. Thus, the valve pocket, as already explained above, in particular in the region of the piston bowl wall formed slightly deeper. This can be accompanied by an increased influence on the swirl flow prevailing in the piston crown. In addition, due to the reduced depth T in the edge region of the piston, the strength of the piston or its architecture is not unduly adversely affected. In addition, the squish flow can be better preserved in the cylinder wall region.
    Advantageously, it may be further in the formation of the valve pocket, when the distance A satisfies the following condition: 0.05 H &lt; = A &lt; = 0.5 H or 0.05 H &lt; = A &lt; = 0.2 H or 0.1 H &lt; = A &lt; = 0.2 H or a + 1 mm &lt; = A &lt; = 20 mm. A further deepening of the whole valve pocket would usually affect the strength of the piston too much or lead to a collision with cooling passages of the piston. If the bottom of the valve pocket, as stated below, is employed, at least in the area of the piston crown recess further depression is possible. Thus, the turbulence entry is increased. It may be advantageous if the valve pocket has a valve pocket bottom with a surface normal N, wherein the surface normal N at least one valve pocket is inclined at an angle ß to the central axis M or the central axis of the corresponding gas exchange valve, with 1 ° &lt; = ß &lt; = 25 ° or 5 ° <= β <= 20 ° or 5 ° <= β <= 10 °, with a distance A increasing towards the bottom of the piston.
    Thus, the valve pocket, as already explained above, at least in some areas, that is, in particular in the region of the piston bottom cup wall, be formed slightly deeper. The valve pocket bottom may be flat, concave, convex or have a hybrid form of the above basic shapes. The surface normal represents at least one zone or only one point on the valve pocket bottom.
    As a rule, the valves or their shank axes are aligned parallel to the piston axis in large engines. If, in this case, a valve pocket is necessary for the clearance of the valve, its valve pocket bottom is oriented at right angles to the shaft axis. There is no reason to hire the valve bag bottom.
    With the use of an engaged or inwardly sloping valve pocket bottom, the distance between the valve and the valve pocket bottom varies in such a large engine. The latter alone to ensure increased turbulence entry. The critical distance to the valve is achieved only in the radially outer region of the valve pocket.
    It can also be advantageous if the valve pocket has a depth T at least in the area of the piston bowl wall, the depth T fulfilling the following condition with respect to the height H: 0.05 H = T <= 0.5 H or 0 , 05 H &lt; = T &lt; = 0.2 H or 0.1 H &lt; = T &lt; = 0.2 H.
    The region of the piston bowl wall is located with respect to the central axis M in the radial direction at the level of the piston bowl wall. With a maximum recessed in the area of the piston bowl wall valve pocket is on the one hand a reinforced
    Turbulence influence on the prevailing in the piston crown cavity swirl flow associated. By this design, the strength of the piston or its architecture is not unduly adversely affected.
    The area of the piston bowl wall, i. the area of the valve pocket located near the piston bowl wall can be arranged at the level of the piston bowl wall in the radial direction to the central axis M. The minimum distance a between the valve pocket or a valve pocket bottom and the corresponding gas exchange valve may depend on the size of the engine of its Blendraumarchitektur and experience be between 0.5 mm and 3 mm, at least in the operating condition. When cold or when switched off, the distance may be slightly greater.
    Creating the squish flow and increasing the swirl flow can have a positive effect on combustion. However, this can be even more positive if these directed flows are purposefully converted to turbulence, as this would further enhance combustion.
    Brief description of the drawing
    Further advantages and details of the present disclosure are explained in the patent claims and in the description and illustrated in the figures. In the drawing show:
    Figure 1 is a perspective view of the piston;
    Figure 2 is a sectional view of the piston;
    Figure 3 is a schematic diagram of an engine.
    Detailed description
    A piston 1 shown in FIG. 1 has a piston skirt 1.1 and a piston skirt 2 bounding the piston skirt 1.1 upwards. The piston head 2 is formed from a piston bottom edge 2.1 and a coaxially to a central axis M extending piston bottom trough 2.2. The piston bottom trough 2.2 has a piston bottom 4 limiting the bottom of the piston bottom 2.2 and a piston trough wall 3 adjoining the bottom of the piston trough 4. Within the piston bowl edge 2.1 four distributed over the circumference arranged valve pockets 5.1 to 5.4 are provided.
    As shown in Fig. 2, the respective valve pocket 5.1 to 5.4 with respect to the central axis M on the one hand and with respect to a valve axis 6.3, 6.4 on the other hand, employed valve pocket bottom 5a-5d. A surface normal N formed on the respective valve pocket bottom 5a-5d encloses an angle β of approximately 7 degrees with the central axis M or with the respective axis of the gas exchange valve 6.3, 6.4. Starting from a distance a, which has the respective gas exchange valve 6.1, 6.2 to the piston head 2.1 and the valve pocket bottom 5a-5d, this distance a shown in FIG. 2, right side, increases continuously to a distance A, and it is in the range Piston well wall 3 or in the radial direction to the central axis M at the height of the piston bowl wall 3 maximum.
    Correspondingly, a deep T of the respective valve pocket 5.1 in the edge region of the piston 1 with Τ 'is substantially less than a depth T in the region of the piston bowl wall 3.
    The depth T is about 15% of the height H of the piston bottom mold 2.2. The ratio of the height H of the piston bottom trough 2.2 to the diameter D of the piston head 2 and the piston diameter D is about 0.2. The ratio of the bowl diameter d to the diameter D of the piston head 2 is about 0.5.
    According to FIG. 2, the piston 1 also has a cooling channel 7, which is located in the region below the piston bottom edge 2.1.
    The piston 1 according to FIG. 2 is part of a motor or engine block 6.
    According to FIG. 3, six of the above-described pistons 1, 1 'are arranged within the engine 6 or a cylinder block (not shown) with corresponding gas exchange valves 6.1', 6.2.
    Industrial Applicability
    The piston and engine block as described herein may be used in a diesel engine or in a gasoline engine or gasoline engine. In the case of the Otto engine or Otto gas engine, the engine may be formed with an external or internal mixture formation.
    A piston according to the present disclosure may be configured so that improved combustion is achieved.
    As described herein, according to an exemplary embodiment of the present disclosure, at least one valve pocket may be at least partially formed substantially deeper than is necessary for the clearance of the opened gas exchange valve.
    权利要求:
    Claims (8)
    [1]
    1. piston (1) of an internal combustion engine with a central axis M having a piston skirt (1.1); and a piston skirt (2) with a diameter D which delimits the piston skirt (1.1) upwards, wherein the piston crown (2) is formed from a piston crown edge (2.1) and a piston crown (2.2) with a piston bowl wall (3) having a height H, wherein in the piston bottom edge (2.1) at least one valve pocket (5.1-5.4) is recessed, with respect to the piston bottom edge (2.1) has a valve pocket depth T, wherein the depth T with respect to the height H at least in the region of the piston bowl wall (3) satisfies the following condition: 0.05 H &lt; = T &lt; = 0.5 H.
    [2]
    2. Piston (1) according to claim 1, wherein the valve pocket (5.1-5.4) has a valve pocket bottom (5a-5d) with a surface normal N, wherein the surface normal N at least one valve pocket (5.1-5.4) by an angle ß inclined to the central axis M is disposed at 1 ° &lt; = β &lt; = 25 °, whereby the depth T increases towards the piston bottom well (2.2).
    [3]
    3. engine block (6) of an internal combustion engine with a piston guided therein (1) having a piston skirt (1.1) with center axis M; and a piston head (2) which delimits the piston skirt (1.1) upwardly with a diameter D, wherein the piston head (2) is formed from a piston bottom edge (2.1) and a piston bottom depression (2.2) with a piston depression wall (H) ( 3), at least one valve pocket (5.1) formed in the piston bottom edge (2.1); with at least one gas exchange valve (6.1, 6.2), which has a central axis (6.3, 6.4) and a minimum distance a from the piston bottom cavity (2.2) to ensure clearance of the opened gas exchange valve (6.1), at least one valve pocket (5.1-5.4) , At least partially, is designed substantially deeper than for the clearance of the open gas exchange valve (6.1, 6.2) is necessary, wherein the distance a at least in the region of the piston bowl wall (3) is increased to a distance A, with


    [4]
    4. engine block (6) according to claim 3, wherein the distance A satisfies the following condition:


    [5]
    5. Motor block (6) according to claim 3 or 4, wherein the valve pocket (5.1-5.4) has a valve pocket bottom (5a-5d) with a surface normal N, wherein the surface normal N at least one valve pocket (5.1-5.4) inclined by an angle ß to the central axis M or to the central axis (6.3, 6.4) of the gas exchange valve (6.1, 6.2) is arranged, with 1 ° <= ß <= 25 °, with a distance A to the piston crown (2.2) increases.
    [6]
    6. engine block (6) according to one of claims 3 to 5, wherein the valve pocket (5.1-5.4) at least in the region of the piston bowl wall (3) has a depth T, the depth T with respect to the height H satisfies the following condition:


    [7]
    7. Diesel engine (6) or gasoline engine (6) or Otto gas engine (6) with a piston guided therein (1) according to one of claims 1 or 2.
    [8]
    8. Diesel engine (6) or gasoline engine (6) or Otto gas engine (6) with an engine block according to one of claims 3 to 6.
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    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
    DE201210103212|DE102012103212A1|2012-04-13|2012-04-13|Piston of an internal combustion engine|
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