EP3334918A1 - Piston pour moteur à combustion interne - Google Patents

Piston pour moteur à combustion interne

Info

Publication number
EP3334918A1
EP3334918A1 EP16757179.3A EP16757179A EP3334918A1 EP 3334918 A1 EP3334918 A1 EP 3334918A1 EP 16757179 A EP16757179 A EP 16757179A EP 3334918 A1 EP3334918 A1 EP 3334918A1
Authority
EP
European Patent Office
Prior art keywords
piston
pressure side
center line
pin bore
distance
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.)
Pending
Application number
EP16757179.3A
Other languages
German (de)
English (en)
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
Original Assignee
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/fr
Pending legal-status Critical Current

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
    • 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 claim 1.
  • a piston for internal combustion engines is known from the generic DE 197 40 065 A1.
  • the hubs are reset in the bolt axis direction such that the outer hub clearance is 60% to 65% of the piston diameter or less.
  • the hub outer surfaces, which connect the two sliding surfaces have a linear (linear) course over the height of the sliding surfaces.
  • the hub outer surfaces also called box walls
  • the hub outer surfaces are not basically flat, but also curved, both in sections parallel and perpendicular to the piston axis.
  • the curvature of the surface in sections perpendicular to the piston axis is always the same for the entire surface of the box wall. This results in upward (in the direction of the piston head) decreasing distance of the box walls an upward decreasing width of the bearing sliding surface.
  • DE 197 40 065 A1 thus discloses a light metal piston for internal combustion engines with a roof-shaped piston crown with a combustion bowl, the hubs are reset in the bolt axis direction, wherein the outer hub distance is 60% to 65% of the piston diameter or less, and wherein above the outer surfaces of the recessed hubs provided in the circumferential direction an angle between 45 ° and 60 ° enclosing open cavity extending in the direction of the piston head in the area behind the ring field, and wherein the hub inner surfaces trapezoidal or stepped stepped, and the shaft length is 40% to 45% of the piston diameter).
  • a piston is known from DE 101 45 589 A1.
  • This has a piston crown, which consists of a ring field with a plurality of annular grooves and optionally a combustion bowl.
  • a piston shaft is arranged below the piston head, said piston shaft consists of two the piston in operation in the internal combustion engine bearing shaft wall sections, which serve to guide the piston in the cylinder of the internal combustion engine.
  • the shaft wall sections are connected to each other via past connecting walls, wherein the connecting walls have no connection to the running surface of the cylinder.
  • the connecting walls have a curved course, which may be convex, concave or a combination of these curvatures. Furthermore, in this known piston in the region of the connecting walls of the lower edge of the ring field over this protruding formed (supernatant) and there at least partially hollowed out, so that a space for weight saving arises.
  • the invention is based on the object to produce a piston for an internal combustion engine while reducing the piston mass and improved stress distribution in the box region of the piston.
  • the piston has on its pressure side a box wall spacing of the box walls between 35% and 51% of the piston diameter and / or that the piston has on its counterpressure side a box wall spacing of the box walls between 26% and 39% of the piston diameter.
  • Pressure side is called the piston or cylinder side, on which the piston is supported during combustion.
  • the pressure side is opposite to the Direction of rotation of the crankshaft.
  • Counterpressure side is the pressure side opposite piston or cylinder side.
  • the inventively designed shank support a more homogeneous stress distribution is achieved within the piston. It can thus be made even larger ring field intersections.
  • the mass of the piston is significantly reduced, but at the same time meets the requirements of current internal combustion engines with the highest thermal and mechanical loads.
  • the invention provides that the piston has on its pressure side a box wall spacing of the box walls between 40% and 51%, preferably between 46% and 49% of the piston diameter. Also, the invention provides that the piston on its counter-pressure side has a box wall spacing of the box walls between 30% and 39%, preferably between 34% and 37% of the piston diameter. As a result, the box walls move closer to each other, which leads to further material savings. Smaller piston faces on the pressure side and counterpressure side of the piston reduce 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. Further, the invention provides that the distance between the top edge of the land land and the vertex the free space parallel to the pin bore axis is smaller than the extension of the top land.
  • 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 invention provides that a distance between a center line of the box wall on the counter-pressure side and center line of the piston transverse to the pin bore axis is less than the distance between the center line of the box wall on the pressure side and the center line of the piston transversely to the pin bore axis.
  • the invention provides that a distance between the center line of the box wall on the counter-pressure side and center line of the piston transverse to the pin bore axis at the periphery of the piston is less than the distance between the center line of the box wall on the counter-pressure side and center line of the piston transverse to the pin bore axis.
  • the invention provides that a position of an intersection between the distance between the center line of the box wall on the pressure side and the center line of the piston transversely to the pin bore axis and the center line of the box wall 10% to 35%, preferably 15% to 30%, in particular 20% to 25% of the piston diameter.
  • the curved hub in conjunction with the newly designed shaft connection makes it possible, by the resulting ground support, to minimize stresses in the combustion bowl in highly-charged direct-injection internal combustion engines.
  • the wall thickness of the piston crown could be reduced by up to 30%. As a result, a reduction in the mass of the piston is achieved.
  • Fig. 1 is a view of a piston according to the prior art DE 10 2005
  • Fig. 2 is a sectional view of a piston according to the prior art DE
  • Fig. 3 is a sectional view from below of a piston according to the invention
  • FIG. 4 shows a further sectional view from below of the piston according to FIG. 3
  • FIG. 3 5 is a further sectional view from below of the piston according to Figure 3
  • Fig. 6 is a side sectional view (counter-pressure side) of the piston according to
  • FIG. 3 the outline of a piston according to FIG. 2, FIG.
  • FIG. 7 is a side sectional view (pressure side) of the piston according to Figure 3 and for comparison the outline of a piston of FIG. 2,
  • Fig. 8 is a side sectional view (counter-pressure side) of the piston according to
  • Fig. 9 is a side sectional view (back pressure side) of the piston according to
  • FIG. 2 is a diagrammatic representation of FIG. 1
  • Fig. 1 1 is a sectional view of the piston according to Figure 3 transversely to
  • Fig. 12 is a sectional view of the piston of Figure 3 outside the
  • Fig. 13 is a sectional view of a piston according to Figure 3 along the
  • FIG. 1 shows a view of a piston 101 according to the prior art DE 10 2005 041 002 A1
  • FIG. 2 shows a sectional view of the piston 101.
  • a piston 101 consists of a piston skirt 102 with an attached piston crown 103, wherein piston skirt 102 and piston crown 103 are integrally formed or consist of two parts which are assembled after their manufacture.
  • the piston 101 moves during operation of the internal combustion engine in a cylinder, not shown, along a piston stroke axis 1 1 1.
  • the piston 101 has a ring field 104 in the As a rule, three annular grooves 109.
  • the piston shaft 102 consists of the piston 1 1 1 supporting shaft wall portions 105, wherein the shaft wall portions 105 are connected by past connecting walls 106 with each other.
  • the connecting walls 106 have a curved course, wherein with respect to the curved course of the connecting walls 106 may be configured differently.
  • the past connecting walls 106 also have a bolt hole 107 for receiving a bolt for connecting the piston 1 1 1 with a connecting rod, not shown.
  • the piston head 103 has an optional combustion bowl 1 10. Furthermore, it is shown that in the region of the piston head 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 region of the annular groove 109 so that a connection from the annular groove 109 into the free space 121 results when the annular groove 109 is introduced into the piston blank.
  • the region of the drainage opening 126 behind the annular groove 109 that is to say in the region of the free space 121, can be cup-shaped.
  • oil can be removed from the surface of the piston 101 or the cylinder running surface in the direction of the inner region of the piston 101 via the drainage opening 126.
  • Drainageo réelle 126 in particular, in each case a Drainageo réelle right and left of the pin bore 107, in particular symmetrically, is located in the region of the past connecting walls 106, since there is sufficient space available for the discharged oil.
  • Figures 3 to 13 show different views of an embodiment of a piston 1 of an internal combustion engine, which may be configured as a lightweight piston, but need not. If it is a lightweight piston, first a piston blank made of a lightweight material, in particular aluminum or an aluminum alloy, poured and then finished, for example, by machining.
  • the basic construction of such a piston 1 consists of a piston shaft 2 with an attached piston head 3, wherein piston skirt 2 and piston crown 3 are integrally formed or consist of two parts which be joined together after their preparation.
  • the piston 1 moves during operation of the internal combustion engine in a cylinder, not shown, along a piston stroke axis 1 1.
  • the piston 1 has a ring field 4 with three annular grooves on the rule.
  • the piston skirt 2 consists of the piston 1 bearing shaft wall sections 5, wherein the skirt wall sections 5 are connected by past connecting walls 6 together.
  • the connecting walls 6 have a curved course, with respect to the curved course of the connecting walls 6 can be configured differently. 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 piston stroke axis 11), since this course is particularly important in terms of mass saving while at the same time maintaining the required strength.
  • the past connecting walls 6 further have a pin bore 7 for receiving a bolt for connecting the piston 1 with a connecting rod, not shown. Within the pin bore 7 a pin bore axis 8 is shown.
  • the piston head 3 has an optional combustion bowl 10. Furthermore, it is shown that in the region of the piston head 3 behind the ring field 4 and above the pin bore 7, a free space 21 is present.
  • FIG. 3 shows a sectional view from below of a piston 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 end faces 17 and the box wall 14 in an upper vertex 19.
  • the pressure side 12 of the piston 1 is shown and below the counter-pressure side thirteenth
  • the course and / or the extent of the curvature 24 also has the advantage that a free space 21 is created in the interior of the piston, which is connectable to the play demand of a Trapezplepleuels, not shown, via which the piston 1 with the crankshaft, also not shown , is required.
  • R1 denotes the radius of the box wall 14 above the pin bore 7. With R2 the radius of the box wall 14 is on the pressure side 12 of the piston 1 designated. R3 in turn represents the radius of the box wall 14 on the counter-pressure side 13 of the piston. 1
  • FIG. 4 shows a further sectional view from below of the piston 1 according to FIG. 3.
  • the position of the box wall 14 in the lower vertex 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 are plotted on the back pressure side 13.
  • FIG. 5 shows yet another sectional view from below of the piston 1 according to FIG. 3, here the position of the box wall 14 in the lower vertex 18 is shown.
  • A 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 is referred to transversely 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 represents 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 transversely to the pin bore axis 8.
  • D is 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 first transverse to the pin bore axis 8 on the circumference of the piston.
  • FIG. 6 shows a lateral sectional view (counterpressure side 13) of the piston 1 according to FIG. 3 and, for comparison, the outline of a piston 101 according to FIG. 2, to show the position of the box wall 14.
  • FIG. 7 shows a lateral view 2 shows the contour of a piston 101 according to FIG.
  • the box walls 14 are narrower than previously customary lightweight piston as they are known from DE 10 2005 041 002 A1.
  • X1 a distance between the box walls on the counter-pressure side according to DE 10 2005 041 002 A1 is designated.
  • X2 indicates the distance between the box walls on the counter-pressure side according to the embodiment of Figure 3.
  • ⁇ 1 represents the distance between the box walls on the pressure side according to DE 10 2005 041 002 A1.”
  • ⁇ 2 "again represents the distance between the box walls on the Print page according to the embodiment of Figure 3 is.
  • FIG. 8 shows a lateral sectional view (pressure side 12) of the piston 1 according to FIG. 3
  • FIG. 9 shows a lateral sectional view (pressure side 12) of the piston 1 according to FIG. 3, the position of the box wall 14 being clearly recognizable Box walls 14, a reduction of a pull-out bevel 22 is realized for the casting tool inserts. This in turn allows an enlargement of the free spaces 21 compared to lightweight pistons, as they are known from DE 10 2005 041 002 A1, which leads to a further mass reduction.
  • W1 denotes the angle of the pull-out bevel 22 on the pressure side 12 of the piston 1. With “W2”, the angle of the pull-out bevel 22 is marked on the counter-pressure side 13 of the piston 1.
  • FIG. 10 shows a bottom view of the piston 1 according to FIG.
  • the piston 1 has smaller skirt surfaces in the region of the skirt wall sections 5 on the pressure side 12 and on the counter-pressure side 13 to reduce the friction.
  • pistons for internal combustion engines with crankshaft offset compensation of the shank surfaces is to be made according to the resulting lateral forces.
  • Shown is a box wall clearance 27 on the pressure side 12 and a box wall distance 28 on the counter-pressure side 13.
  • the piston diameter 20 is located.
  • the pressure side 12 has a distance of the shaft surfaces or box wall spacing 27 between 46% and 51% of the piston diameter 20.
  • On the counter-pressure side 13 is a distance of the shank surfaces or a Kastenwandabstand 28 between 34% and 39% of the piston diameter 20 before.
  • FIG. 1 1 shows a sectional view of the piston 1 according to FIG. 3 transversely to the pin bore axis 8 and FIG. 12 shows a sectional view of the piston 1 according to FIG. 3 outside the pin bore axis 8.
  • Shown is a Feuersteg 29, 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 land 29 and the apex 30 of the clearance 21 across the pinhole axis 8.
  • Y in turn forms the distance between the upper edge of the land 29 and the apex 30 of the clearance 21 parallel to the pinhole axis 8 from.
  • 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 conditions FS> X and FS> Y apply
  • FIG. 13 shows a sectional view of a piston 1 according to FIG. 3 along the pin bore axis 8, a further feature being apparent for mass reduction.
  • the radial depth of a lifting groove 23 has the dimension Z with a value of 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)

Abstract

L'invention concerne un piston (1) pour un moteur à combustion interne, comprenant une tige de piston (2) et un fond de piston (3) comportant un champ annulaire (4) et agencé sur celui-ci. La tige de piston (2) comporte des sections de paroi de tige (5) porteuses et des parois de caisson (14) en retrait, qui relient les sections de paroi de tige (5) les unes aux autres et qui présentent un profil courbé ainsi qu'un alésage d'axe (7). Un espace libre (21) en dégagement dans la zone du fond de piston (3) est présent au-dessous du champ annulaire (4) dans la zone de l'alésage d'axe (7). Le piston (1) comporte une face de pression (12) et une face de contre-pression (13), le piston (1) présentant, sur sa face de pression (12), un écart (27) entre les parois de caisson (14) compris entre 35 % et 51 % du diamètre de piston (20) et/ou le piston (1) présentant, sur sa face de contre-pression (13), un écart (28) entre les parois de caisson (14) compris entre 26 % et 39 % du diamètre de piston (20).
EP16757179.3A 2015-08-11 2016-08-11 Piston pour moteur à combustion interne Pending EP3334918A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102015215313 2015-08-11
PCT/EP2016/069170 WO2017025608A1 (fr) 2015-08-11 2016-08-11 Piston pour moteur à combustion interne

Publications (1)

Publication Number Publication Date
EP3334918A1 true EP3334918A1 (fr) 2018-06-20

Family

ID=56801511

Family Applications (1)

Application Number Title Priority Date Filing Date
EP16757179.3A Pending EP3334918A1 (fr) 2015-08-11 2016-08-11 Piston pour moteur à combustion interne

Country Status (6)

Country Link
US (1) US10823109B2 (fr)
EP (1) EP3334918A1 (fr)
JP (1) JP2018525562A (fr)
CN (1) CN108026860A (fr)
DE (1) DE102016114957A1 (fr)
WO (1) WO2017025608A1 (fr)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2019096827A1 (fr) 2017-11-14 2019-05-23 Ks Kolbenschmidt Gmbh Piston en acier à design optimisé
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
WO2021013788A1 (fr) * 2019-07-19 2021-01-28 Ks Kolbenschmidt Gmbh Piston pour un moteur à combustion interne, avec réduction de la puissance de frottement

Family Cites Families (18)

* Cited by examiner, † Cited by third party
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 (fr) * 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
JP2002332912A (ja) * 2001-04-30 2002-11-22 Honda Motor Co Ltd 内燃機関用ピストン
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
WO2013138261A1 (fr) 2012-03-12 2013-09-19 Federal-Mogul Corporation Piston de moteur
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
JP2016535191A (ja) * 2013-10-14 2016-11-10 カーエス コルベンシュミット ゲゼルシャフト ミット ベシュレンクテル ハフツングＫＳ Ｋｏｌｂｅｎｓｃｈｍｉｄｔ ＧｍｂＨ 内燃機関用のピストン及びその製造方法
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

Also Published As

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

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