EP3334918B1 - Kolben für eine brennkraftmaschine - Google Patents

Kolben für eine brennkraftmaschine Download PDF

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Publication number
EP3334918B1
EP3334918B1 EP16757179.3A EP16757179A EP3334918B1 EP 3334918 B1 EP3334918 B1 EP 3334918B1 EP 16757179 A EP16757179 A EP 16757179A EP 3334918 B1 EP3334918 B1 EP 3334918B1
Authority
EP
European Patent Office
Prior art keywords
piston
pressure side
distance
center line
box wall
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.)
Active
Application number
EP16757179.3A
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German (de)
English (en)
French (fr)
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EP3334918A1 (de
Inventor
Klaus Lormes
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
KS Kolbenschmidt GmbH
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KS Kolbenschmidt GmbH
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by KS Kolbenschmidt GmbH filed Critical KS Kolbenschmidt GmbH
Publication of EP3334918A1 publication Critical patent/EP3334918A1/de
Application granted granted Critical
Publication of EP3334918B1 publication Critical patent/EP3334918B1/de
Active legal-status Critical Current
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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
    • 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 
    • F02F2003/0007—Monolithic pistons; One piece constructions; Casting of pistons
    • 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 
    • F02F3/26—Pistons  having combustion chamber in piston head

Definitions

  • the invention relates to a piston for an internal combustion engine according to the features of the preamble of patent claim 1.
  • a piston for internal combustion engines is from the generic DE 197 40 065 A1 known.
  • the hubs are set back in the direction of the pin axis in such a way that the outer hub distance is 60% to 65% of the piston diameter or less.
  • the hub outer surfaces that connect the two sliding surfaces have a straight (linear) course over the height of the sliding surfaces.
  • the hub outer surfaces also called box walls
  • the hub outer surfaces are not fundamentally flat, but also curved, both in sections parallel and perpendicular to the piston axis.
  • the direction of curvature of the surface in sections perpendicular to the piston axis is always the same for the entire area of the box wall. This results in a width of the supporting sliding surface that decreases towards the top (towards the piston crown) as the distance between the box walls decreases.
  • the DE 197 40 065 A1 thus discloses a light metal piston for internal combustion engines with a roof-shaped piston crown with a combustion chamber recess, wherein the hubs are set back in the direction of the pin axis such that the outer hub distance is 60% to 65% of the piston diameter or less, and wherein above the outer surfaces of the set-back hubs an open cavity is provided which encloses an angle between 45° and 60° in the circumferential direction and extends in the direction of the piston crown into the area behind the ring field, and wherein the hub inner surfaces trapezoidal or stepped, and the shaft length is 40% to 45% of the piston diameter).
  • a piston from the DE 101 45 589 A1 known.
  • This has a piston crown, which consists of an annular field with several annular grooves and, if necessary, a combustion chamber bowl.
  • a piston skirt is arranged below the piston crown in the direction of movement of the piston, whereby this piston skirt consists of two skirt wall sections that support the piston during operation in the internal combustion engine and serve to guide the piston in the cylinder of the internal combustion engine.
  • the skirt wall sections are connected to one another via recessed connecting walls, whereby the connecting walls have no connection to the running surface of the cylinder.
  • the connecting walls have a curved shape that can be convex, concave or a combination of these curvatures. Furthermore, in this known piston, the lower edge of the ring field is designed to protrude over the connecting walls (overhang) and is at least partially hollowed out there, so that a free space is created for the purpose of saving weight.
  • the US 2002/0178909 A1 describes a piston for an internal combustion engine having a crown, a pair of piston pin projections each integrated into the crown and facing each other, and a pair of skirt walls each integrated into the crown and facing each other, a lower end of the pair of skirt walls being on top of a lower end of the pair of piston pin projections.
  • the invention is based on the object of producing a piston for an internal combustion engine with a reduction in the piston mass and improved stress distribution in the box area of the piston.
  • the piston on its pressure side has a box wall distance of the box walls between 35% and 51% of the piston diameter and/or that the piston on its counterpressure side has a box wall distance of the box walls between 26% and 39% of the piston diameter.
  • the pressure side is the side of the piston or cylinder on which the piston rests during combustion.
  • the pressure side is opposite to the direction of rotation of the crankshaft.
  • the counterpressure side is the side of the piston or cylinder opposite the pressure side.
  • the skirt support designed according to the invention achieves a more homogeneous distribution of stress within the piston. This means that even larger ring field undercuts can be made.
  • the mass of the piston is significantly reduced, but at the same time it can withstand the requirements of current internal combustion engines with the highest thermal and mechanical loads.
  • the invention provides that the piston on its pressure side has a box wall distance of between 40% and 51%, preferably between 46% and 49% of the piston diameter.
  • the invention also provides that the piston on its counterpressure side has a box wall distance of between 30% and 39%, preferably between 34% and 37% of the piston diameter. This brings the box walls closer together, which leads to further material savings. Smaller skirt areas on the pressure side and counterpressure side of the piston lead to a reduction in friction.
  • the invention provides that a distance between an upper edge of a top land and a vertex of a free space transverse to a pin bore axis of the piston is smaller than the extent of the top land. Furthermore, the invention provides that the distance between the upper edge of the top land and the vertex of the free space parallel to the pin bore axis is smaller than the extent of the top land.
  • the invention provides that the distance between the upper edge of the top land and the apex of the free space transverse to the pin bore axis of the piston and/or a distance between the upper edge of the top land and the apex of the free space parallel to the pin bore axis are between 50% and 95%, preferably between 65% and 90%, smaller than the extent of the top land. This achieves a material saving and a reduction in the piston mass.
  • a radial depth of a lifting groove has a dimension of greater than or equal to 2 millimeters (mm), preferably greater than or equal to 3 mm, in particular greater than or equal to 4 mm.
  • the invention provides that a distance between a center line of the box wall on the pressure side and a center line of the piston transverse to the pin bore axis is greater than a distance between a center line of the box wall on the pressure side and the center line of the piston transverse to the pin bore axis on the circumference of the piston.
  • the box walls designed according to the invention have reduced the draft angle for the casting tool inserts. This in turn enables the free space behind the ring area to be increased, which leads to a reduction in the piston mass.
  • the invention provides that a distance between a center line of the box wall on the counterpressure side and the center line of the piston transverse to the pin bore axis is smaller than the distance between the center line of the box wall on the pressure side and the center line of the piston transverse to the pin bore axis.
  • the box walls designed according to the invention have made it possible to reduce the draft angle for the casting tool inserts. This in turn enables an increase in the free space behind the ring field, which leads to a reduction in the piston mass.
  • the invention provides that a distance between the center line of the box wall on the counter-pressure side and the center line of the piston transverse to the pin bore axis on the circumference of the piston is smaller than the distance between the center line of the box wall on the counter-pressure side and the center line of the piston transverse to the pin bore axis.
  • the box walls designed according to the invention have made it possible to reduce the draft angle for the casting tool inserts. This in turn enables an increase in the free space behind the ring area, which leads to a reduction in the piston mass.
  • the invention provides that a position of an intersection point between the distance between the center line of the box wall on the pressure side and the center line of the piston transverse to the pin bore axis and the center line of the box wall is 10% to 35%, preferably 15% to 30%, in particular 20% to 25% of the piston diameter.
  • the curved hub in connection With the newly designed shaft connection, the resulting floor support makes it possible to minimize stresses in the combustion chamber bowl in highly charged direct injection internal combustion engines.
  • the wall thickness of the piston crown could be reduced by up to 30%. This achieves a reduction in the mass of the piston.
  • the Figure 1 shows a view of a piston 101 according to the prior art DE 10 2005 041 002 A1
  • the Figure 2 shows a sectional view of the piston 101.
  • a piston 101 consists of a piston shaft 102 with an attached piston head 103, whereby the piston shaft 102 and the piston head 103 are formed in one piece or consist of two parts that are joined together after they have been manufactured.
  • the piston 101 moves in a cylinder (not shown) along a piston stroke axis 111.
  • the piston 101 also has an annular field 104 with, as a rule, three annular grooves 109.
  • the piston skirt 102 consists of skirt wall sections 105 supporting the piston 111, the skirt wall sections 105 being connected to one another by recessed connecting walls 106.
  • the connecting walls 106 have a curved profile, and the curved profile of the connecting walls 106 can be designed in different ways.
  • the recessed connecting walls 106 also have a pin bore 107 for receiving a pin for connecting the piston 111 to a connecting rod (not shown).
  • the piston crown 103 has an optional combustion chamber recess 110. Furthermore, it is shown that in the area of the piston crown 3, behind the ring field 104 and above the pin bore 107, there is a free space 121.
  • a drainage opening 126 is shown.
  • the drainage opening 126 is arranged in the area of the annular groove 109, so that a connection from the annular groove 109 to the free space 121 is created when the annular groove 109 is introduced into the piston blank.
  • the area of the drainage opening 126 behind the annular groove 109 i.e. in the area of the free space 121, can be cup-shaped.
  • oil can be drained from the surface of the piston 101 or the cylinder running surface in the direction of the inner area of the piston 101 via the drainage opening 126.
  • the drainage opening 126 in which in particular a drainage opening is arranged to the right and left of the pin bore 107, in particular symmetrically, is located in the area of the rear connecting walls 106, since there is sufficient space here for the drained oil.
  • FIGS. 3 to 13 show various views of an embodiment of a piston 1 of an internal combustion engine, which can be designed as a lightweight piston, but does not have to be.
  • a piston blank is first cast from a lightweight material, in particular aluminum or an aluminum alloy, and then finished, for example by machining.
  • the basic construction of such a piston 1 consists of a piston skirt 2 with an attached piston head 3, wherein the piston skirt 2 and piston head 3 are formed in one piece or consist of two parts that are joined together after they have been manufactured.
  • the piston 1 moves in a cylinder (not shown) along a piston stroke axis 11.
  • the piston 1 also has an annular field 4 with, as a rule, three annular grooves.
  • the piston shaft 2 consists of shaft wall sections 5 supporting the piston 1, wherein the shaft wall sections 5 are connected to one another by recessed connecting walls 6.
  • the connecting walls 6 have a curved course, wherein the curved course of the connecting walls 6 can be designed in different ways. Reference is made to this curved course (concave and/or convex from one skirt wall section to the other skirt wall section and/or in its course in the piston stroke axis 11), since this course is particularly important in terms of saving mass while maintaining the required strength.
  • the rear connecting walls 6 also have a pin bore 7 for receiving a pin for connecting the piston 1 to a connecting rod (not shown). A pin bore axis 8 is shown within the pin bore 7.
  • the piston crown 3 has an optional combustion chamber bowl 10. It is also shown that in the area of the piston crown 3, behind the ring field 4 and above the pin bore 7, there is a free space 21.
  • the Figure 3 shows a sectional view from below of a piston 1 according to the invention.
  • a curvature 24 of the box wall 14 in a lower vertex 18 is opposite to a curvature 26 of inner hub faces 17 and the box wall 14 in an upper vertex 19.
  • the pressure side 12 of the piston 1 is shown at the top and the counterpressure side 13 at the bottom.
  • the course and/or extent of the curvature 24 also has the advantage that a free space 21 is created in the interior of the piston 1, which is necessary for the clearance requirement of a trapezoidal connecting rod (not shown), via which the piston 1 can be connected to the crankshaft (also not shown).
  • R1 indicates the radius of the box wall 14 above the bolt hole 7.
  • R2 indicates the radius of the box wall 14 on the pressure side 12 of the piston 1.
  • R3 in turn stands for the radius of the box wall 14 on the counterpressure side 13 of the piston 1.
  • the Figure 4 shows a further sectional view from below of the piston 1 according to Figure 3.
  • the position of the box wall 14 in the lower apex 18 is shown.
  • the center line 15 of the box wall 14 on the pressure side 12 of the piston 1 and the center line 16 of the box wall 14 on the counterpressure side 13 are marked.
  • the Figure 5 shows yet another sectional view from below of the piston 1 according to Figure 3 , here the position of the box wall 14 in the lower vertex 18 is shown.
  • A indicates the distance between the center line 15 of the box wall 14 on the pressure side 12 and the center line 25 of the piston 1 transverse to the pin bore axis 8.
  • B indicates the distance between the center line 15 of the box wall 14 on the pressure side 12 and the center line 25 of the piston 1 transverse to the pin bore axis 8 on the circumference of the piston 1.
  • C stands for the distance between the center line 16 of the box wall 14 on the counter-pressure side 13 and center line 25 of the piston transverse to the pin bore axis 8.
  • D is the distance between center line 16 of the box wall 14 on the counter-pressure side 13 and center line 25 of the piston 1 transverse to the pin bore axis 8 on the circumference of the piston 1.
  • Positions of the intersection points with the applicable conditions Position of intersection point A: 20% to 25% of the piston diameter 20
  • Position of intersection point B B ⁇ A
  • Position of intersection point C C ⁇ A
  • Position of intersection point D D ⁇ C
  • the Figure 6 shows a side sectional view (counterpressure side 13) of the piston 1 according to Figure 3 and for comparison the outline of a piston 101 according to Fig. 2 , to show the position of the box wall 14.
  • the Figure 7 shows a side sectional view (pressure side 12) of the piston 1 according to Figure 3 and for comparison the outline of a piston 101 according to Fig. 2 , to show the position of the box wall 14.
  • the piston 1 has free spaces 21 behind the ring field 4.
  • the box walls 14 are closer together than in previously conventional lightweight pistons such as those from the DE 10 2005 041 002 A1 are known.
  • X1 is a distance between the box walls on the counter pressure side according to DE 10 2005 041 002 A1
  • X2 indicates the distance between the box walls on the counterpressure side according to the embodiment from Figure 3
  • Y1 represents the distance between the box walls on the pressure side according to DE 10 2005 041 002 A1
  • Y2 in turn represents the distance between the box walls on the pressure side according to the embodiment from Figure 3 represents.
  • the Figure 8 shows a side sectional view (pressure side 12) of the piston 1 according to Figure 3 and the Figure 9 shows a side sectional view (pressure side 12) of the piston 1 according to Figure 3 , the position of the box wall 14 is clearly visible.
  • the newly designed box walls 14 reduce the draft angle 22 for the casting tool inserts. This in turn enables an increase in the clearances 21 compared to lightweight pistons, as is evident from the DE 10 2005 041 002 A1 known, which leads to a further mass reduction.
  • W1 designates the angle of the extension bevel 22 on the pressure side 12 of the piston 1.
  • W2 designates the angle of the extension bevel 22 on the counterpressure side 13 of the piston 1.
  • FIG 10 is a bottom view of the piston 1 according to Figure 3
  • the piston 1 has smaller skirt surfaces in the area of the skirt wall sections 5 on the pressure side 12 and on the counter-pressure side 13 to reduce friction.
  • the skirt surfaces In the case of pistons for internal combustion engines with crankshaft offset, the skirt surfaces must be compensated in accordance with the resulting lateral forces.
  • a box wall distance 27 on the pressure side is shown. 12 and a box wall distance 28 on the counter pressure side 13.
  • the piston diameter 20 is shown.
  • the pressure side 12 has a distance between the shaft surfaces or box wall distance 27 of between 46% and 51% of the piston diameter 20.
  • the distance between the shaft surfaces or box wall distance 28 is between 34% and 39% of the piston diameter 20.
  • the Figure 11 shows a sectional view of the piston 1 according to Figure 3 transverse to the bolt bore axis 8 and the Figure 12 shows a sectional view of the piston 1 according to Figure 3 outside the pin bore axis 8, the features for reducing the mass of the piston 1 are shown here.
  • a top land 29 is shown, which forms a vertex 30 at its greatest extent in the direction of the piston crown 3.
  • X describes the distance between the upper edge of the top land 29 and the apex 30 of the free space 21 transverse to the bolt bore axis 8.
  • Y in turn represents the distance between the upper edge of the top land 29 and the apex 30 of the free space 21 parallel to the bolt bore axis 8.
  • FS represents the dimension of the top land 29.
  • the dimension X and/or the dimension Y are smaller than the dimension FS, preferably between 65% and 90%.
  • the Figure 13 shows a sectional view of a piston 1 according to Figure 3 along the bolt bore axis 8, another feature for reducing mass can be seen.
  • the radial depth of a lifting groove 23 has the dimension Z with a value greater than or equal to 4 mm.

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)
EP16757179.3A 2015-08-11 2016-08-11 Kolben für eine brennkraftmaschine Active EP3334918B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102015215313 2015-08-11
PCT/EP2016/069170 WO2017025608A1 (de) 2015-08-11 2016-08-11 Kolben für eine brennkraftmaschine

Publications (2)

Publication Number Publication Date
EP3334918A1 EP3334918A1 (de) 2018-06-20
EP3334918B1 true EP3334918B1 (de) 2024-12-18

Family

ID=56801511

Family Applications (1)

Application Number Title Priority Date Filing Date
EP16757179.3A Active EP3334918B1 (de) 2015-08-11 2016-08-11 Kolben für eine brennkraftmaschine

Country Status (7)

Country Link
US (1) US10823109B2 (pl)
EP (1) EP3334918B1 (pl)
JP (1) JP2018525562A (pl)
CN (1) CN108026860A (pl)
DE (1) DE102016114957A1 (pl)
PL (1) PL3334918T3 (pl)
WO (1) WO2017025608A1 (pl)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3710686B1 (de) 2017-11-14 2026-02-25 KS Kolbenschmidt GmbH Stahlkolben mit optimiertem design
JP2019173722A (ja) * 2018-03-29 2019-10-10 アート金属工業株式会社 内燃機関用ピストン
DE102019203650A1 (de) * 2019-03-18 2020-09-24 Mahle Lnternational Gmbh Kolben für eine Brennkraftmaschine
DE102019209248A1 (de) * 2019-06-26 2020-12-31 Federal-Mogul Nürnberg GmbH Kolben für einen Verbrennungsmotor
CN114630953B (zh) * 2019-07-19 2024-03-01 Ks科尔本施密特有限公司 用于内燃机的具有摩擦损失降低的活塞
DE102023122676B3 (de) 2023-08-24 2025-02-13 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Kolbeneinrichtung für eine Brennkraftmaschine insbesondere für ein Kraftfahrzeug

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20020178909A1 (en) * 2001-04-30 2002-12-05 Akifumi Nomura Piston for internal combustion engine

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Publication number Priority date Publication date Assignee Title
DE1974065U (de) 1967-09-02 1967-12-07 Max Pietsch Fabrik Fuer Strass Klumpenzerkleinerungs-einrichtung fuer streumaschinen.
JPH0299245U (pl) * 1989-01-24 1990-08-07
DE19740065A1 (de) * 1997-09-12 1999-03-18 Ks Kolbenschmidt Gmbh Leichtmetallkolben für Brennkraftmaschinen
JP2002317691A (ja) 2001-04-19 2002-10-31 Unisia Jecs Corp 内燃機関のピストン
DE10145589B4 (de) 2001-09-15 2006-09-14 Ks Kolbenschmidt Gmbh Kolben für eine Brennkraftmaschine
DE102005041002A1 (de) 2005-08-29 2007-03-01 Ks Kolbenschmidt Gmbh Leichtbaukolben
DE102006027810A1 (de) * 2006-06-16 2007-12-20 Mahle International Gmbh Verfahren zur Herstellung eines einteiligen Kolbens sowie damit hergestellter Kolben
DE102007031581A1 (de) * 2007-07-06 2009-01-08 Ks Kolbenschmidt Gmbh Kolben einer Brennkraftmaschine mit einer erhöhten Schrägstellung der Kastenwände des Kolbens
JP5640706B2 (ja) * 2010-12-07 2014-12-17 トヨタ自動車株式会社 ピストンおよび内燃機関
DE102011080822A1 (de) * 2011-08-11 2013-02-14 Mahle International Gmbh Kolben
DE102011085448A1 (de) * 2011-10-28 2013-05-02 Ks Kolbenschmidt Gmbh Kolben und Pleuel für eine Brennkraftmaschine
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
JP5994512B2 (ja) * 2012-09-19 2016-09-21 スズキ株式会社 内燃機関用ピストン
JP2014062507A (ja) * 2012-09-21 2014-04-10 Suzuki Motor Corp 内燃機関用ピストン
KR20180004290A (ko) * 2013-10-14 2018-01-10 카에스 콜벤슈미트 게엠베하 내연기관용 피스톤 및 그 제조방법
CN204327307U (zh) * 2014-11-19 2015-05-13 山东滨州渤海活塞股份有限公司 用于汽油机的轻量化降噪音活塞
CN204851463U (zh) * 2015-07-23 2015-12-09 重庆长安汽车股份有限公司 一种新型轻量化活塞

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US20020178909A1 (en) * 2001-04-30 2002-12-05 Akifumi Nomura Piston for internal combustion engine

Also Published As

Publication number Publication date
US20180306139A1 (en) 2018-10-25
DE102016114957A1 (de) 2017-02-16
WO2017025608A1 (de) 2017-02-16
US10823109B2 (en) 2020-11-03
JP2018525562A (ja) 2018-09-06
CN108026860A (zh) 2018-05-11
EP3334918A1 (de) 2018-06-20
PL3334918T3 (pl) 2025-03-24

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