EP0356457A1 - Leichtmetall-tauchkolben für verbrennungsmotoren. - Google Patents
Leichtmetall-tauchkolben für verbrennungsmotoren.Info
- Publication number
- EP0356457A1 EP0356457A1 EP88903796A EP88903796A EP0356457A1 EP 0356457 A1 EP0356457 A1 EP 0356457A1 EP 88903796 A EP88903796 A EP 88903796A EP 88903796 A EP88903796 A EP 88903796A EP 0356457 A1 EP0356457 A1 EP 0356457A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- piston
- pressure side
- shaft
- light metal
- counter
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
- F02F3/00—Pistons
- F02F3/02—Pistons having means for accommodating or controlling heat expansion
- F02F3/022—Pistons having means for accommodating or controlling heat expansion the pistons having an oval circumference or non-cylindrical shaped skirts, e.g. oval
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
- F02F3/00—Pistons
- F02F3/02—Pistons having means for accommodating or controlling heat expansion
- F02F3/04—Pistons having means for accommodating or controlling heat expansion having expansion-controlling inserts
- F02F3/042—Pistons having means for accommodating or controlling heat expansion having expansion-controlling inserts the inserts consisting of reinforcements in the skirt interconnecting separate wall parts, e.g. rods or strips
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
- F05C2201/00—Metals
- F05C2201/02—Light metals
- F05C2201/021—Aluminium
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
- F05C2201/00—Metals
- F05C2201/04—Heavy metals
- F05C2201/0433—Iron group; Ferrous alloys, e.g. steel
- F05C2201/0448—Steel
Definitions
- the invention relates to a light metal plunger for internal combustion engines according to the preamble of claim 1.
- the object of the invention is Reasons to further reduce the noise generation in the generic piston, which is caused by the piston head striking against the cylinder liner on the counter-pressure side when the piston is cold.
- the piston assumes in the cold state in the engine cylinder a position in which the piston head is inclined with its upper end on the pressure side relative to the cylinder running surface in such a way that the play in the land area is opposite the cylinder running surface on the counter pressure side is larger than on the pressure side.
- the specified inclination of the piston head in the cold state of the piston in the engine cylinder is achieved in that the lateral surface on the counterpressure side of is inclined upwards downwards with respect to the piston longitudinal axis, specifically with the radial distance decreasing towards the lower piston shaft end with respect to the piston axis.
- the abutment of the piston on the lateral surface so inclined on the counter pressure side is further favored by the inclination of the shaft surface area there on the pressure side in the opposite direction. This statement in turn relates to the cold state.
- the control strip inserted on the counter pressure side in the upper end area of the skirt causes a hindrance to the thermal expansion of the light metal in this area of the skirt, while the lower counter pressure side area of the skirt can expand considerably more freely without a control strip.
- the surface line on the counterpressure side of the shaft in full-load operation of the engine is given a course which is aligned essentially parallel to the longitudinal axis of the piston head. So that the Kolbe ⁇ kopf then runs centrally in the cylinder bore.
- the further control strip provided on the pressure side in the lower shaft region exerts an influence in the same direction. This ensures that a larger radial distance the skirt surface area in the control strip area to the longitudinal piston axis compared to the overlying shaft area on the counter-pressure side, a system in the lower shaft area is additionally favored.
- a common measure for reducing piston noise in the engine running is to unlock the hub bore of the piston.
- This roofing is usually on the print side.
- a tilting moment arises at the top dead center of the compression stroke when combustion starts, which pushes the piston head in the direction of the counter pressure side.
- the lower shaft area of the piston on the counter pressure side is pressed radially outwards.
- the piston skirt on the counter-pressure side should in turn be relatively stiff in order to ensure the radial distance of the lateral surface from the longitudinal axis of the piston head, which is greater in the cold state compared to the lower area, and not due to excessive elastic deformability in the latter Restrict area again.
- the different stiffnesses can be determined by the size of the unsupported arch length of the shaft on the pressure side and counter pressure side vary.
- these measures consist, in particular, in the provision of a transverse slot between the piston head and the piston skirt on the counter-pressure side and in the provision of a control strip in the upper region of the piston skirt exclusively on the counter-pressure side and, if appropriate, an additional control strip in the lower region the pressure side of the shaft half.
- Fig. 2 shows the axial surface course of the cold and warm piston skirt according to Fig. 1 on the counter pressure side
- Fig. 3 shows the axial generatrix of the cold and warm piston skirt according to Fig. 1 on the pressure side
- Fig. 4 shows the oblique orientation of the cold
- FIG. 5 shows the orientation of the warm piston shaft according to FIG. 1 during engine operation within the engine cylinder
- Fig. 6 is a view of the piston of FIG. 1 from below
- Fig. 8 shows the polar surface line course (cold and warm condition) of the piston skirt in plane VIII
- Fig. 9 shows a second embodiment of a piston in longitudinal section
- Fig. 10 shows the axial generatrix of the cold and warm piston skirt according to Fig. 9 on the counter pressure side
- Fig. 11 shows the axial generatrix of the cold and warm piston skirt according to Fig. 9 on the pressure side
- Fig. 12 is a view of the piston of FIG. 9 from below
- Fig. 13 shows a section through the piston in the plane XIII
- Fig. 14 shows a section through the piston in the plane XIV
- the piston consists of an aluminum-silicon alloy. In its head part there are ring grooves 1 for compression rings and an underlying groove 2 provided for an oil control ring.
- A average shaft height below the lowest
- Ring groove in a circumferential area of approximately the same shaft height of at least 90 degrees from the pressure and counter pressure side
- X longitudinal axis of the piston determined by the piston head
- the shaft of the piston is separated from the piston head on the counter pressure side by a transverse slot 3.
- the transverse slot 3 extends in the circumferential direction over a total of 90 degrees, symmetrically on both sides of the plane running through the longitudinal axis X in the pressure-counter pressure direction.
- a control strip 4 made of steel is used exclusively on the counter pressure side in the interior of the shaft in the upper region thereof. The control effect emanating from this control strip when the piston heats up is measured to a maximum of about 50 my with piston diameters between 70 and 100 mm.
- FIG. 4 shows the position of the piston according to FIG. 1, which it takes up in the cold state in the engine cylinder during the compression stroke. Due to the conrod angle during this stroke, the piston rests with its shaft on the counter pressure side during the downward movement. The alignment takes place in the area of the piston skirt on the counterpressure side through the axial surface line which is present there and extends in a straight line over a larger area. The straight lateral surface course extends there from the lower end of the shaft to approximately 1% before the upper end of the shaft.
- the axial surface profile is essentially spherical on the pressure side. When the piston tilts back from the counterpressure side to the pressure side in the top dead center position of the piston, the piston can roll smoothly on the pressure-side spherical shaft shape. This achieves an additional improvement in piston noise.
- the decisive noise reduction lies in the fact that the circumference of the piston head on the counter-pressure side is sufficiently distant from the cylinder running surface due to the stem inclined there. so as not to hit the cylinder wall under partial load or when the engine is not yet warm.
- the inclination of the axial surface line of the shaft on the counter-pressure side is selected to such an extent that in full-load operation, the control effect of the control strip 4 results in a parallel profile of this surface line to the longitudinal axis X.
- the control strip 4 is attached directly to the upper end of the shaft and in the example shown extends over a height of 25% of the total shaft length.
- the diameter of the top land of the piston head is ge ringer as ⁇ the maximum diameter of Kolbenschaf ⁇ tes.
- Fig. 4 shows quite clearly how the piston head is brought into such an inclined position by the shaft when the piston is cold, that the play between the ring portion and the cylinder running surface on the counterpressure side of the piston is significantly greater than on the diametrically opposite pressure side of the piston. This prevents the ring portion from striking the piston noise.
- control strips 4 and 5 each extend because of one of the two hubs 6 areas circumferentially up to the piston tilt plane running perpendicular to the piston pin axis, ie the control strips are circumferentially separated from one another in the area of the piston tilt plane.
- control strips 4 and 5 are connected to a common control strip 7 connected in the region of the piston hub 6.
- the piston By means of the regulating tires 5 in the lower shaft area on the pressure side, the piston can be installed in this lower shaft area in the cold state with a radial play so narrow there that on the counter pressure side an attachment to the shaft jacket which is inclined there from top to bottom is promoted. As a result, the piston comes into contact earlier with the pressure-side underside of the shaft when tilting to the counter pressure side, as a result of which the tilt angle is reduced.
- the stiffness of the piston skirt is changed over the axial height in that the load-bearing skirt surfaces are unevenly circumferentially wide and are each supported radially inwards at the circumferential end.
- the different elasticity in the axial direction is distributed in such a way that the piston skirt on the counter pressure side in the upper area, in which the control strip 4 is located, is stiffer than in the shaft area underneath.
- the lower shaft area is stiffer than the lower shaft area opposite on the counter pressure side.
- the walls 10 connecting the load-bearing shaft surfaces 8, 9 in the direction of the piston axis are predetermined by the shape of the load-bearing surfaces 8, 9 which change over the height of the shaft.
- the hubs 6 can protrude radially beyond these walls 10.
- a narrow circumferential collar 11 can be provided for manufacturing reasons. Such a collar enables the piston to be transported in a rolling manner through the individual production stations.
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Pistons, Piston Rings, And Cylinders (AREA)
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE3713242A DE3713242C1 (de) | 1987-04-18 | 1987-04-18 | Leichtmetall-Tauchkolben fuer Verbrennungsmotoren |
DE3713242 | 1987-04-18 |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0356457A1 true EP0356457A1 (de) | 1990-03-07 |
EP0356457B1 EP0356457B1 (de) | 1991-02-27 |
Family
ID=6325934
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP88903796A Expired - Lifetime EP0356457B1 (de) | 1987-04-18 | 1988-04-15 | Leichtmetall-tauchkolben für verbrennungsmotoren |
Country Status (6)
Country | Link |
---|---|
US (1) | US5000078A (de) |
EP (1) | EP0356457B1 (de) |
JP (1) | JP2690340B2 (de) |
BR (1) | BR8807471A (de) |
DE (2) | DE3713242C1 (de) |
WO (1) | WO1988008078A1 (de) |
Families Citing this family (20)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE3843761A1 (de) * | 1988-12-24 | 1990-07-05 | Mahle Gmbh | Leichter tauchkolben fuer verbrennungsmotoren |
DE58906955D1 (de) * | 1988-12-24 | 1994-03-24 | Mahle Gmbh | Leichter tauchkolben für verbrennungsmotoren. |
DE3843866A1 (de) * | 1988-12-24 | 1990-06-28 | Mahle Gmbh | Leichter tauchkolben fuer verbrennungsmotoren |
DE3931949A1 (de) * | 1989-09-25 | 1991-04-04 | Alcan Gmbh | Kolben fuer einen verbrennungsmotor |
US5107807A (en) * | 1989-09-28 | 1992-04-28 | Nissan Motor Company, Ltd. | Piston for internal combustion engine |
DE4109160C3 (de) * | 1991-03-20 | 2000-11-30 | Federal Mogul Nuernberg Gmbh | Kolben für Brennkraftmaschinen |
JPH11303674A (ja) | 1998-04-24 | 1999-11-02 | Unisia Jecs Corp | 内燃機関のピストン |
US7293497B2 (en) | 2005-11-03 | 2007-11-13 | Dresser, Inc. | Piston |
US7302884B2 (en) * | 2005-11-03 | 2007-12-04 | Dresser, Inc. | Piston |
DE102008029071B4 (de) * | 2008-06-10 | 2019-12-24 | Dr. Ing. H.C. F. Porsche Aktiengesellschaft | Kolben für eine Brennkraftmaschine |
DE102008002536B4 (de) * | 2008-06-19 | 2015-02-12 | Federal-Mogul Nürnberg GmbH | Kolben für einen Verbrennungsmotor |
DE102009032379A1 (de) * | 2008-08-13 | 2010-02-18 | Mahle International Gmbh | Kolben für einen Verbrennungsmotor |
DE102011080822A1 (de) | 2011-08-11 | 2013-02-14 | Mahle International Gmbh | Kolben |
US10753310B2 (en) | 2012-02-10 | 2020-08-25 | Tenneco Inc. | Piston with enhanced cooling gallery |
JP2015511676A (ja) | 2012-03-12 | 2015-04-20 | フェデラル−モーグル コーポレイション | エンジンピストン |
DE112013005725T5 (de) * | 2012-11-30 | 2015-08-13 | Cummins Ip, Inc. | Motorzylinder- und Laufbuchsenbaugruppe |
DE102013009164A1 (de) * | 2013-05-31 | 2014-12-04 | Mahle International Gmbh | Kolben für einen Verbrennungsmotor |
US9759156B2 (en) * | 2015-03-04 | 2017-09-12 | Mahle International Gmbh | Asymmetric piston |
US20170254291A1 (en) * | 2016-03-02 | 2017-09-07 | Federal-Mogul Llc | Galleryless piston with slotted ring groove |
JP2018145861A (ja) * | 2017-03-06 | 2018-09-20 | 日野自動車株式会社 | ピストン構造 |
Family Cites Families (11)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1825750A (en) * | 1926-10-25 | 1931-10-06 | Cleveland Trust Co | Piston |
US2086677A (en) * | 1934-07-19 | 1937-07-13 | Adolph L Nelson | Piston |
US2110346A (en) * | 1934-07-31 | 1938-03-08 | Perfect Circle Co | Piston |
FR812385A (fr) * | 1936-07-20 | 1937-05-08 | Monsieur Friedrich Richard Die | Piston en métal léger à jupe en une seule pièce |
US2551488A (en) * | 1948-02-18 | 1951-05-01 | Thompson Prod Inc | Controlled expansion piston |
GB1256242A (en) * | 1968-09-05 | 1971-12-08 | Ass Eng Ltd | Improvements in pistons |
US3908521A (en) * | 1972-07-31 | 1975-09-30 | Hepworth & Grandage Ltd | Pistons for internal combustion engines or for compressors |
GB1505148A (en) * | 1975-08-12 | 1978-03-30 | Hepworth & Grandage Ltd | Pistons |
JPS5781144A (en) * | 1980-11-10 | 1982-05-21 | Yamaha Motor Co Ltd | Piston for internal combustion engine |
DE3430132A1 (de) * | 1984-08-16 | 1986-02-27 | Mahle Gmbh, 7000 Stuttgart | Aluminium-tauchkolben fuer verbrennungsmotoren mit regelstreifen |
JPH0750049Y2 (ja) * | 1986-11-25 | 1995-11-15 | イズミ工業株式会社 | 熱膨張抑制ピストン用ストラット |
-
1987
- 1987-04-18 US US07/424,243 patent/US5000078A/en not_active Expired - Fee Related
- 1987-04-18 DE DE3713242A patent/DE3713242C1/de not_active Expired
-
1988
- 1988-04-15 DE DE8888903796T patent/DE3861855D1/de not_active Expired - Fee Related
- 1988-04-15 JP JP63503659A patent/JP2690340B2/ja not_active Expired - Lifetime
- 1988-04-15 EP EP88903796A patent/EP0356457B1/de not_active Expired - Lifetime
- 1988-04-15 WO PCT/EP1988/000321 patent/WO1988008078A1/de active IP Right Grant
- 1988-04-15 BR BR888807471A patent/BR8807471A/pt not_active IP Right Cessation
Non-Patent Citations (1)
Title |
---|
See references of WO8808078A1 * |
Also Published As
Publication number | Publication date |
---|---|
BR8807471A (pt) | 1990-05-22 |
JPH02503104A (ja) | 1990-09-27 |
EP0356457B1 (de) | 1991-02-27 |
DE3713242C1 (de) | 1988-10-20 |
US5000078A (en) | 1991-03-19 |
JP2690340B2 (ja) | 1997-12-10 |
DE3861855D1 (de) | 1991-04-04 |
WO1988008078A1 (fr) | 1988-10-20 |
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