Abstract
A cylinder housing for a reciprocating-piston internal combustion engine, in particular of a motor vehicle, includes a first cylinder which is delimited by a first cylinder barrel and a second cylinder which is delimited by a second cylinder barrel. The cylinders differ from one another with respect to their respective inner contour formed by the respective cylinder barrels.
Claims
1. A cylinder housing of a reciprocating internal combustion engine, comprising: a first cylinder delimited by a first cylinder barrel; and a second cylinder delimited by a second cylinder barrel; wherein the first cylinder has a first internal contour formed by the first cylinder barrel and the second cylinder has a second internal contour formed by the second cylinder barrel; wherein the first internal contour is configured to differ from the second internal contour in a cold state of the reciprocating internal combustion engine such that a shape of the first internal contour and a shape of the second internal contour differ from each other and differ from a desired target shape in terms of a respective diameter and/or a respective honing shape of the respective cylinder barrels in the cold state of the reciprocating internal combustion engine, and such that in a fired operation of the reciprocating internal combustion engine the shape of the first internal contour and the shape of the second internal contour correspond to the desired target shape.
Description
BRIEF DESCRIPTION OF THE DRAWINGS
(1) FIG. 1 shows details of a schematic side view of a cylinder housing according to a first embodiment for a reciprocating internal combustion engine, the cylinder housing comprising cylinders which are different from one another in terms of their respective internal contours formed by their respective cylinder barrels;
(2) FIG. 2 shows details of a schematic side view of the cylinder housing according to a second embodiment; and
(3) FIG. 3 shows details of a schematic side view of the cylinder housing according to a third embodiment.
DETAILED DESCRIPTION OF THE DRAWINGS
(4) In the drawings, the same or functionally identical elements are provided with the same reference signs.
(5) FIG. 1 shows details of a schematic side view of a cylinder housing, denoted as a whole by reference sign 10, for a reciprocating internal combustion engine of a motor vehicle, which can be driven by means of the reciprocating internal combustion engine. The reciprocating internal combustion engine comprises, when produced in its entirety, a drive shaft designed as a crankshaft that can rotate about a rotational axis relative to the cylinder housing 10. The crankshaft is mounted, for example, on a crankcase of the reciprocating internal combustion engine so as to be rotatable about a rotational axis relative to the crankcase. The crankcase can be formed in one piece with the cylinder housing 10 such that the cylinder housing 10 is designed as a cylinder crankcase. Alternatively, it is conceivable for the cylinder housing 10 and the crankcase to be formed as separate, interconnected components. The reciprocating internal combustion engine also comprises at least one cylinder head (not shown in the drawings) and is connected, in particular screwed, to the cylinder housing 10.
(6) The cylinder housing 10 comprises a first cylinder 12 and a second cylinder 14 which are combustion chambers of the reciprocating internal combustion engine. In fired operation of the reciprocating internal combustion engine, the fired operation of which is also referred to as ignited operation, combustion processes take place in the cylinders 12 and 14. A piston (not shown in the drawings) is received in each of the cylinders 12 and 14 so as to be translationally movable, each piston being able to move between a bottom dead center (BDC) and a top dead center (TDC). The bottom dead center and the top dead center are dead centers or reversal points at each of which a movement direction of the piston is reversed. By definition, as it travels from the top dead center to the bottom dead center, the piston moves downwards and thereby away from the cylinder head, in particular away from a combustion chamber roof which is formed by the cylinder head and associated with the cylinder in question. As it travels from the bottom dead center to the top dead center, the piston moves upwards and thus towards the cylinder head or the combustion chamber roof.
(7) The pistons are hingedly coupled to the crankshaft by means of respective connecting rods such that the translational movements of the pistons are converted into a rotational movement of the crankshaft about the rotational axis thereof. The pistons are driven by the respective combustion processes taking place in the respective cylinders 12 and 14. In the drawings, the cylinders 12 and 14 are shown together or such that they are mutually overlapping so that any similarities and differences between the cylinders 12 and 14 can be clearly illustrated.
(8) It can be seen from FIG. 1 that the first cylinder 12 is delimited by a first cylinder barrel 16 and the second cylinder 14 is delimited by a second cylinder barrel 18, the respective cylinder barrels 16 and 18 also being referred to as cylinder running surfaces, piston barrels, piston running surfaces or liners. Each piston can be supported in the radial direction thereof against the relevant cylinder barrel 16 or 18 and slide along the relevant cylinder barrel 16 or 18, for example, as it travels from the top dead center to the bottom dead center, and vice versa.
(9) On the left-hand side of FIG. 1, the cylinder housing 10 and thus the cylinder barrels 16 and 18 are in a heated state W, which is achieved, for example, during fired operation or after a certain period of time after fired operation has begun. FIG. 1 shows, in the center and on the right-hand side, a cylinder housing 20 according to a first embodiment in a cold state K and heated state W, respectively, the cylinder housing 20 being explained in more detail below.
(10) The heated state W of the cylinder housing 10 shown on the left-hand side of FIG. 1 is achieved, for example, if no special measures are provided on the barrels 16 and 18 or if the barrels are the same in relation to the cold state thereof, in particular in terms of their honing and/or their diameter. In the cold state, the cylinder barrels 16 and 18 of the cylinder housing 10 which are shown on the left-hand side of FIG. 1 have, for example, at least substantially the same contours, in particular internal contours. Effects or boundary conditions, which will be explained in more detail below, may lead to different distortions of the cylinders 12 and 14 and thus of the cylinder barrels 16 and 18, these distortions also being referred to as cylinder distortions. The effects or boundary conditions mentioned above are, for example, combustion chamber pressures occurring in the cylinders 12 and 14 during fired operation, thermal expansions resulting from the cylinder housing 10 being heated as a result of fired operation and/or screw connections by means of which the cylinder housing 10 is connected to the cylinder head. These boundary conditions or effects may result in cylinder-specific, i.e., cylinder-individual, cylinder distortions such that the cylinders 12 and 14 or the cylinder barrels 16 and 18 and thus the internal contours of the cylinder barrels 16 and 18 may be distorted, i.e., deformed, differently proceeding from the cold state. As a result, the cylinder barrels 16 and 18 have different internal contours in the heated state W shown on the left-hand side of FIG. 1 such that the cylinders 12 and 14 have different shapes at the internal circumference.
(11) These different, cylinder-specific cylinder distortions can lead to drawbacks in terms of the friction power and the noise characteristics of the reciprocating internal combustion engine, since they may result, for example, in unfavorable values for a clearance between each piston and the relevant cylinder barrel 16 or 18. This clearance is also referred to as piston clearance. If, for example, the cylinder-specific cylinder distortions result in an excessively high value for the piston clearance, this may result in undesired noises being generated, since, for example, contact alteration of the piston against the relevant cylinder barrel 16 or 18 can lead to noises. If, for example, the cylinder-specific cylinder distortions result in excessively low values for the piston clearance, this may result in overlapping states between the piston and the relevant cylinder barrel 16 or 18, for example. This results in the reciprocating internal combustion engine having excessively high friction power, and this may result in high fuel consumption and high CO.sub.2 emissions.
(12) From the cylinder housing 20 shown in FIG. 1, the function and purpose of which corresponds to the function and purpose of the cylinder housing 10, it can be seen that the cylinder barrels 16 and 18 and thus the cylinders 12 and 14 are different from one another in the cold state K in terms of their respective internal contours 22, 24 formed by the respective cylinder barrels 16, 18. According to the first embodiment, linear shape correction by means of trumpet honing is provided, the cylinder barrels 16 and 18 being different from one another in the cold state K in terms of their specific trumpet honing and/or in terms of their respective diameters.
(13) FIG. 1 shows, on the right-hand side, the heated state W of the cylinder barrels 16 and 18 of the cylinder housing 20 which are shown in the center of FIG. 1, on which the above-mentioned special measures are provided, by special machining, in the form of the different trumpet honing and/or the different diameters. The heated state shown on the right-hand side of FIG. 1 results from the combination of the cylinder barrels 16 and 18 or the internal contours 22 and 24 shown on the left-hand side of and in the center of FIG. 1. It can be seen from FIG. 1 that, in the heated state W shown on the right-hand side, the cylinder barrels 16 and 18 or the internal contours 22 and 24 thereof are at least brought closer to a desired course 19 which indicates a target shape and thus a desired course or a desired shape for the relevant cylinder barrel 16 or 18. In particular, the course 19 indicates a desired trumpet shape which can be produced by the above-mentioned trumpet honing, optionally in combination with a cold clearance adjustment.
(14) In other words: In order to optimize or compensate for the cylinder-specific cylinder distortions in the cylinder housing 20 and thus in order for it to be possible for the reciprocating internal combustion engine to be operated in a particularly efficient manner and for the reciprocating internal combustion engine to have particularly advantageous noise characteristics, in the cylinder housing 20, the cylinders 12 and 14 are different from one another, in particular in the cold state K, in terms of their respective internal contours 22 and 24 formed by the respective cylinder barrels 16 and 18. In other words, the cylinders 12 and 14 are different from one another at ambient temperature in terms of their respective internal contours 22 and 24 formed by the respective cylinder barrels 16 and 18, the shapes of the internal contours 22 and 24 becoming alike, for example, due to the respective cylinders 12 and 14 being heated as a result of fired operation.
(15) In the first embodiment, as can be seen in the center of FIG. 1, the different, cylinder-specific cylinder distortions of zero order are linearly corrected. Each internal contour 22 and 24 widens downwards in an axial direction of the cylinder 12 and 14, respectively, in a specific portion. Therefore, each internal contour 22 and 24 widens in a direction in which the piston moves as it travels from the top dead center to the bottom dead center. Each internal contour 22 and 24 is produced, for example, by conical trumpet honing. As a result of the different internal contours 22 and 24, the internal contours 22 and 24 also differ from one another in terms of at least one particular internal diameter, the particular internal diameter can also be referred to as the cylinder diameter. As a result of using the cylinder-specific trumpet honing and the particular cylinder-specific diameter, an at least substantially optimum piston clearance can be set, such that excessive friction power and the generation of undesired noises can be prevented.
(16) It can also be seen from FIG. 1 that, for example, each internal contour 22 and 24 widens downwards over the entire axial extension thereof. The cylinder housing 10 or 20 is supported against or connected to the cylinder head, at least indirectly, by means of a joint face 25, for example. In the first embodiment illustrated in FIG. 1, the widening of the internal contour 22 and 24 and thus the trumpet shape starts at the joint face 25. In the first embodiment, each internal contour 22 and 24 has an at least substantially linear course, as a result of which differences of zero order between the cylinder distortions can be corrected. As a result of a non-linear course of each internal contour 22 and 24 in the cold state K, differences of a higher order between the cylinder distortions can be corrected. Each internal contour 22 and 24 may widen downwards, this widening also beginning at the joint face 25 in the second embodiment.
(17) FIG. 2 shows a second embodiment of the cylinder housing 20, with the cylinder housing 10 also being visible in FIG. 2. Here, the cylinder housing 10 or 20 comprises, for example, four cylinders 12, 14, 26 and 28. The cylinder 12 comprises the cylinder barrel 16, the cylinder 14 comprises the cylinder barrel 18, the cylinder 26 comprises a cylinder barrel 30, and the cylinder 28 comprises a cylinder barrel 32.
(18) In order to compensate for the cylinder-specific distortions of the cylinders 12, 14, 26 and 28, as in the second and third embodiments, in the cylinder housing 20, the cylinders 12, 14, 26 and 28 are different from one another in terms of their respective internal contours 22, 24, 34 and 36 formed by the respective cylinder barrels 16, 18, 30 and 32. FIG. 2 shows the cylinder housing 10 and 20 in the heated state denoted by reference sign W in FIG. 2, with FIG. 2 also showing the cylinder housing 20 in the cold state denoted by reference sign K.
(19) In the cylinder housing 20, radial widening in combination with linear trumpet honing is provided in the cold state K such that each internal contour 22, 24, 34 and 36 widens downwards at least substantially linearly. As a result of the contours being radially widened to different extents, the differences of zero order in the individual distortions in the cylinder housing 10 or 20 can be corrected. The widening produced by the cylinder-specific trumpet honing begins below the joint face 25.
(20) From FIG. 2, it can be seen that the internal contours 22, 24, 34 and 36 become alike as a result of the cylinders 12, 14, 26 and 28 being heated by fired operation of the reciprocating internal combustion engine, such that, in the heated state W, the internal contours 22, 24, 34 and 36 are very similar or are at least substantially the same or identical. The internal contours 22, 24, 34 and 36 correspond at least substantially to the desired target shape indicated by the course 19 or resemble the target shape to a particularly high extent.
(21) FIG. 3 shows the cylinder housing 20 according to a third embodiment, with FIG. 3 showing the cylinder housing 10 and 20 in the heated state W and the cylinder housing 20 in the cold state K. In the fourth embodiment too, the internal contours 22, 24, 34 and 36 widen downwards, this widening beginning below the joint face 25. Each internal contour 22, 24, 34 and 36, as in the second embodiment, has a non-linear course in order to correct differences of higher orders.
(22) The heated state W of the cylinder housing 10 shown in FIGS. 2 and 3 illustrates the cylinder-specific cylinder distortions of the cylinders 12, 14, 36 and 38 which can be compensated for by the described design of the internal contours 22, 24, 34 and 36 of the cylinder housing 20. Therefore, the heating of the cylinder housing 20 in the heated state W proceeding from the cold state K of the cylinder housing 20 and the cylinder-specific cylinder distortions resulting from this heating lead to the internal contours 22 and 24, 34 and 36 corresponding to the desired target shape indicated by the course 19 in the heated state W.
