EP0356457B1 - Leichtmetall-tauchkolben für verbrennungsmotoren - Google Patents
Leichtmetall-tauchkolben für verbrennungsmotoren Download PDFInfo
- Publication number
- EP0356457B1 EP0356457B1 EP88903796A EP88903796A EP0356457B1 EP 0356457 B1 EP0356457 B1 EP 0356457B1 EP 88903796 A EP88903796 A EP 88903796A EP 88903796 A EP88903796 A EP 88903796A EP 0356457 B1 EP0356457 B1 EP 0356457B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- piston
- skirt
- pressure side
- counter
- light
- 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.)
- Expired - Lifetime
Links
- 239000002184 metal Substances 0.000 title claims description 16
- 238000002485 combustion reaction Methods 0.000 title claims description 6
- 230000006835 compression Effects 0.000 claims description 5
- 238000007906 compression Methods 0.000 claims description 5
- 239000000463 material Substances 0.000 claims 3
- 241001125877 Gobio gobio Species 0.000 claims 1
- 239000008186 active pharmaceutical agent Substances 0.000 description 2
- 230000003247 decreasing effect Effects 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- 229910000676 Si alloy Inorganic materials 0.000 description 1
- 229910000831 Steel Inorganic materials 0.000 description 1
- CSDREXVUYHZDNP-UHFFFAOYSA-N alumanylidynesilicon Chemical compound [Al].[Si] CSDREXVUYHZDNP-UHFFFAOYSA-N 0.000 description 1
- 238000005266 casting Methods 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 230000005489 elastic deformation Effects 0.000 description 1
- 239000003921 oil Substances 0.000 description 1
- 238000005096 rolling process Methods 0.000 description 1
- 239000010959 steel Substances 0.000 description 1
Images
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 same preamble of the two independent claims 1 and 2.
- Such pistons are known from GB-PS 12 56 242.
- a control strip is used at the upper end of the shaft, which has a width that varies over its circumference. The width varies in such a way that the radial thickness of the control strip is the smallest on the pressure side of the piston and the greatest on the counterpressure side. This results in a smaller radial expansion of the upper shaft area on the counter pressure side of the shaft than on the pressure side. Due to the smaller expansion of the upper shaft area on the counter pressure side under temperature, a tight running play of the shaft can be achieved in the cold state. The tighter running play is associated with a reduction in the running noise in the cold state, which is strongly influenced by a striking of the top land on the counter-pressure side against the cylinder liner in the cold state of the engine.
- the object of the invention is to further reduce the noise generation in the generic piston which is caused by the piston head striking against the cylinder liner on the counterpressure 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 there is play in the top land area relative to 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 counter-pressure side surface of is inclined upwards downwards with respect to the piston longitudinal axis, specifically with the radial distance decreasing towards the lower piston end towards 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 lateral surface there, given in the opposite direction on the pressure side. This statement in turn relates to the cold state.
- Advantageous for achieving the inclined position of the piston desired in partial engine load operation is the substantially straight line surface profile over a wide range on the counter pressure side.
- 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 area of the stem on the counter-pressure side can expand considerably more freely without a control strip.
- the surface line on the counterpressure side of the shaft receives a course in full-load operation of the engine, which is aligned essentially parallel to the longitudinal axis of the piston head.
- the piston head then also runs centrally in the cylinder bore.
- the control strip provided on the pressure side in the lower shaft area exerts an influence in the same direction. This ensures that by a greater radial distance the skirt lateral surface in the control strip area to the longitudinal axis of the piston compared to the overlying shaft area on the counterpressure side, a system in the lower shaft area is additionally favored.
- a common measure to reduce piston noise when the engine is running is to debach the piston hub bore.
- This roofing is usually on the print side. This creates a tilting moment 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 stem area of the piston on the counter pressure side is pressed radially outwards. This creates contact forces in the aforementioned shaft areas (counter pressure side above or pressure side bottom) which are to be absorbed with the smallest possible elastic deformation.
- the piston skirt In the upper area of the stem, the piston skirt should be on the.
- the counter-pressure side on the other hand, must be relatively stiff in order to ensure the greater radial distance between the lateral surface and the longitudinal axis of the piston head in the cold state compared to the lower region and not to restrict it again in this region due to excessive elastic deformability.
- the different stiffnesses can be determined by the size of the unsupported arch length of the shaft vary on the pressure and counter pressure side.
- 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 of the pressure-side stem half.
- Unsymmetrical shaft shapes are also known per se from DE 35 27 032 A1, but there are also no references to the specific he inventive design of the shaft to reduce the impact noise of the piston head.
- the piston is made of an aluminum-silicon alloy.
- ring grooves 1 for Kom compression rings and an underlying groove 2 provided for an oil control ring.
- the stem of the piston is separated from the piston head on the counterpressure side by a transverse slot 3.
- the transverse slot 3 extends in the circumferential direction over a total of 90 degrees, namely 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 warms up is measured to a maximum of about 50 my with piston diameters between 70 and 100 mm.
- Fig. 4 the position of the piston according to Fig. 1 is drawn, which it assumes 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. Alignment takes place in the area of the piston skirt on the counterpressure side through the axial surface line existing there in a straight line over a larger area.
- the straight generatrix extends there from the lower end of the shaft to about 15% before the upper end of the shaft.
- the axial generatrix is essentially spherical.
- 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 shaft jacket which is 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 chosen 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 less than the maximum diameter of the piston skirt.
- 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 part from striking the piston, which causes the piston noise.
- control strips 4 and 5 each extend Weil 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 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 inclined from top to bottom is promoted.
- the piston tilts to the counter pressure side, it comes into contact with the underside of the shaft on the pressure side earlier, which reduces the tilt angle.
- the stiffness of the piston shaft is changed over the axial height in that the load-bearing shaft surfaces are unequal in circumference and are 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 skirt area below.
- the lower shaft area is made stiffer than the lower shaft area opposite on the counter pressure side.
- the course of the walls 10 connecting the supporting shaft surfaces 8, 9 in the direction of the piston axis is predetermined by the shape of the 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 at the lower end of the shaft. 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)
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 EP0356457A1 (de) | 1990-03-07 |
EP0356457B1 true 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 (ja) |
EP (1) | EP0356457B1 (ja) |
JP (1) | JP2690340B2 (ja) |
BR (1) | BR8807471A (ja) |
DE (2) | DE3713242C1 (ja) |
WO (1) | WO1988008078A1 (ja) |
Families Citing this family (20)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE3843866A1 (de) * | 1988-12-24 | 1990-06-28 | Mahle Gmbh | Leichter tauchkolben fuer verbrennungsmotoren |
DE3843761A1 (de) * | 1988-12-24 | 1990-07-05 | Mahle Gmbh | Leichter tauchkolben fuer verbrennungsmotoren |
EP0449848B1 (de) * | 1988-12-24 | 1994-02-09 | Mahle GmbH | Leichter tauchkolben für 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 |
US7302884B2 (en) * | 2005-11-03 | 2007-12-04 | Dresser, Inc. | Piston |
US7293497B2 (en) | 2005-11-03 | 2007-11-13 | 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 |
US20160273480A1 (en) * | 2012-11-30 | 2016-09-22 | Cummins Ip, Inc. | Engine cylinder and liner assembly |
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 DE DE3713242A patent/DE3713242C1/de not_active Expired
- 1987-04-18 US US07/424,243 patent/US5000078A/en not_active Expired - Fee Related
-
1988
- 1988-04-15 JP JP63503659A patent/JP2690340B2/ja not_active Expired - Lifetime
- 1988-04-15 DE DE8888903796T patent/DE3861855D1/de not_active Expired - Fee Related
- 1988-04-15 EP EP88903796A patent/EP0356457B1/de not_active Expired - Lifetime
- 1988-04-15 BR BR888807471A patent/BR8807471A/pt not_active IP Right Cessation
- 1988-04-15 WO PCT/EP1988/000321 patent/WO1988008078A1/de active IP Right Grant
Also Published As
Publication number | Publication date |
---|---|
JP2690340B2 (ja) | 1997-12-10 |
BR8807471A (pt) | 1990-05-22 |
JPH02503104A (ja) | 1990-09-27 |
DE3713242C1 (de) | 1988-10-20 |
EP0356457A1 (de) | 1990-03-07 |
DE3861855D1 (de) | 1991-04-04 |
US5000078A (en) | 1991-03-19 |
WO1988008078A1 (fr) | 1988-10-20 |
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