Patent Application
20240318610
The invention relates to a steel piston for an internal combustion engine, which comprises a cooling cavity extending in a rotationally symmetrical manner about the piston axis and at least three annular grooves.
Such steel pistons are known in the prior art and comprise annular grooves that are usually configured solely to accommodate the piston rings. Due to the thermal load on such a piston during engine operation, i.e. particularly high temperatures at the piston crown with simultaneous cooling of the cooling channel, thermal deformations occur which substantially curve the piston crown upward and bend the ring zone outward. Owing to the bending of the ring zone, in particular the second annular groove is bent together, i.e. the groove flanks come closer to one another at the end thereof. If a weld seam is placed in the region of the second groove as a result of friction or induction welding, the increase in stiffness due to the additional material of the weld bead leads to high stresses at the transition between the cooling channel wall and the weld bead and at the groove base radii of the second groove. These thermal stresses can lead to crack formations and piston failure under thermal alternating stress.
Until now, attempts have been made to prevent this by shifting the axial position of the weld seam along the piston stroke axis or increasing the wall thickness between the cooling channel and the ring zone. However, the former measure is not always expedient, and the latter measure disadvantageously increases the weight.
DE 197 16 702 C2, which shows a cooling channel located at the level of the first annular groove, and DE 27 34 519 A1 and EP 0 366 983 B1, which do not show a cooling channel, constitute further prior art. It should be noted that none of the cited documents relates to a steel piston.
Against this background, a steel piston is provided having improved resistance to thermomechanical stress in the region of the weld bead and the second groove without increasing the weight.
According thereto, a third annular groove, as viewed from the piston crown, has a greater depth than a second annular groove, and/or a minimum wall thickness between the third annular groove and a cooling cavity extending in a rotationally symmetrical manner about the piston axis is at least locally smaller than a minimum wall thickness between the second annular groove and the cooling cavity. Both measures substantially lead to the third annular groove acting as a bending joint, so to speak, and absorbing a higher proportion of the thermally induced deformation of the ring zone. This relieves the second annular groove, in the region of which a weld seam, and in particular in the case of friction welding the associated weld bead, is typically present. However, it is also conceivable to join piston parts by means of resistance welding or laser welding. The reduced wall thickness can in particular be provided by a local increase in the cross-section of the cooling cavity, for example by means of a turned groove provided there.
In other words, the third annular groove, which until now has only been dimensioned to accommodate an oil ring and therefore typically has a shallower depth than the second annular groove, is deepened in a novel manner and/or the wall thickness to a cooling cavity is locally reduced, which improves the response of the piston to thermal loads. In particular, the stresses in the region of the weld bead and the second annular groove can be reduced, and at the same time the stresses in the region of the third annular groove can be kept within manageable limits.
In particular, as a result of the measure according to the invention, a reduction in stress in the region of the second annular groove of up to 16% could be determined in simulations.
Advantageous embodiments of the steel piston according to the invention are described.
As mentioned, the improved steel piston particularly exhibits its advantages if there is a weld bead or weld seam between the first and third annular grooves, so that there is an additional concentration of stress in this region that can be relieved by the bending about the groove base of the third annular groove, which is accepted according to the invention.
Owing to the deepening of the third annular groove, the bending of this groove increases in an intended manner, which, however, leads to higher stresses in the groove base radii of the third groove. This increase in stress can be compensated by increasing the radii. It is currently in particular preferred that at least one groove base radius of the third annular groove is larger than at least one groove base radius of the second annular groove.
The effects of the last-described measures can be used particularly extensively if the third annular groove has a groove base radius at both the lower flank and the upper flank, each of which is larger than the respective groove base radius of the second annular groove.
Stresses can be limited in a similar manner if the third annular groove has a groove base radius that is elliptical in cross-section or composed of two radii.
In particular, the groove base of the groove may as a whole consist of an elliptical curve that tangentially transitions into lower and upper flanks.
Good results are furthermore achieved with a groove base of the third annular groove that consists of a tangentially continuous transition of at least two radii at the lower flank, a straight section and at least two radii at the upper flank. In mathematical terms, a basket arch is, in other words, described in cross-section.
Furthermore, the two groove base radii of the third groove can each be replaced by a convex cubic spline curve and a curvature-continuous transition to the groove flanks.
Such a steel piston also makes it possible, due to the increased depth of the third annular groove, to dispense with oil drainage holes that are otherwise usually provided in the region of the third annular groove. In particular, oil can be stored in the deeper groove on the downstroke, which can be used again on the upstroke to lubricate the piston skirt.
Finally, in order to particularly ensure the effect according to the invention, it is preferred that the third annular groove has a depth at least 5% greater than the second annular groove. In general, it should be added with regard to described depths and depth ratios that the depth is determined based on the distance between the piston outer wall (imagined in the region of the respective groove) and the deepest point of the groove.
In the following, the invention will be explained in more detail in reference to embodiments shown in the drawing in which:
A steel piston 10 comprises a piston crown 28 with a combustion chamber bowl 26 and a cooling cavity extending in a rotationally symmetrical manner about the piston axis, which is configured as an annular cooling channel 20. Three annular grooves 12, 14, 16 are formed in the region of a ring zone, as viewed from the piston crown. As is apparent in particular in
Furthermore, the wall thickness D3 between the third annular groove 16 and the cooling channel 20 is less than the wall thickness D2 between the second annular groove 14 and the cooling channel 20. In contrast to the other figures,
In the embodiment according to
In addition, an outer weld bead 18 is apparent in the figures, which leads to a stiffening of the material in the shown position in the region of the second annular groove 14, the stress on which can be reduced in an advantageous manner also in the event of thermal deformation by the design of the third annular groove 16 according to the invention. There is furthermore an inner weld bead 19. It should be understood that the outer weld bead 18 shown in the figures does not have to be arranged in the center of the second annular groove 14.
| Number | Date | Country | Kind |
|---|---|---|---|
| 10 2021 207 405.7 | Jul 2021 | DE | national |
| Filing Document | Filing Date | Country | Kind |
|---|---|---|---|
| PCT/EP2022/068725 | 7/6/2022 | WO |
