EP2890883B1 - Piston - Google Patents

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Publication number
EP2890883B1
EP2890883B1 EP13753156.2A EP13753156A EP2890883B1 EP 2890883 B1 EP2890883 B1 EP 2890883B1 EP 13753156 A EP13753156 A EP 13753156A EP 2890883 B1 EP2890883 B1 EP 2890883B1
Authority
EP
European Patent Office
Prior art keywords
piston
cooling channel
section
cross
contraction
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.)
Not-in-force
Application number
EP13753156.2A
Other languages
German (de)
English (en)
Other versions
EP2890883A2 (fr
Inventor
Ulrich Bischofberger
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.)
Mahle International GmbH
Original Assignee
Mahle International 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 Mahle International GmbH filed Critical Mahle International GmbH
Publication of EP2890883A2 publication Critical patent/EP2890883A2/fr
Application granted granted Critical
Publication of EP2890883B1 publication Critical patent/EP2890883B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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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 
    • F02F3/16—Pistons  having cooling means
    • F02F3/20—Pistons  having cooling means the means being a fluid flowing through or along piston
    • F02F3/22—Pistons  having cooling means the means being a fluid flowing through or along piston the fluid being liquid

Definitions

  • the present invention relates to a piston for an internal combustion engine, with a piston head and a piston skirt and with a ring portion and a cooling channel, according to the preamble of claim 1.
  • a generic piston is for example from the DE 10 2006 056 013 A1 known.
  • the piston comprises a piston head and a piston stem projecting therefrom, the piston head having a ring portion in which, in particular, piston rings can be arranged.
  • a circumferential ring carrier is also provided in the region of the ring part. Due to the prevailing in or on the piston thermodynamic conditions, in particular the high temperatures, the piston is also provided with a circumferential cooling channel.
  • the cooling channel is arranged at a distance from the piston crown and from the ring section within the piston. The disadvantage here is that such an arrangement of the cooling channel is a limitation for the size of a piston recess on the piston crown.
  • Similar pistons can also be the AT 003 210 U1 , of the DE 10 2006 013 884 A1 , of the JP 2009-215978 A as well as the JP 1182738 A remove.
  • a ring carrier for a piston of an internal combustion engine is from the DE 101 34 293 A1 known.
  • a sheet metal part of the ring carrier is open to a ring carrier part of the ring carrier to form a cooling channel together with the ring carrier part.
  • the applicant is an aluminum piston with a cooling channel is known, which is formed with a central constriction.
  • the cooling channel is formed by a casting process in the piston and arranged radially within a ring carrier and spatially separated therefrom.
  • the present invention addresses the problem of providing a piston of the generic type an improved or at least alternative embodiment, which is characterized in particular by improved cooling and / or by the possibility of forming a larger piston recess.
  • the present invention is based on the general idea to arrange the cooling channel of the piston for an internal combustion engine at least partially directly to the ring part and in particular on the ring carrier of the piston and thus on the one hand to create space for forming a larger piston recess and on the other hand, the cooling, especially in the region of the ring section , to improve.
  • the cooling channel of the piston is formed so that it has a taper in cross-section approximately centrally.
  • the piston according to the invention thus has a cooling channel, which is formed circumferentially in a piston head of the piston and has a substantially central cross-sectional taper.
  • the piston head further comprises said circumferential ring portion, in which said ring carrier, which is also circumferential, is arranged.
  • the ring carrier now forms a wall section of the cooling channel, so that the cooling channel is arranged at least in regions directly on the ring carrier is and is in direct contact with it.
  • the cooling channel is arranged at least in regions directly on the ring carrier is and is in direct contact with it.
  • improved cooling in this area is ensured by the direct coupling of the cooling channel with the ring carrier.
  • an improved cooling of the piston is achieved in the region of the piston recess, since the piston recess can be formed closer to the cooling channel, and the cooling channel can be placed closer to the piston crown.
  • the special design of the cooling channel with the approximately centrally disposed circumferential taper serves in particular to achieve an improved heat transfer and thus the better cooling of the piston. In this case, this cross section is given along the axial direction of the piston
  • the cooling channel has a constriction along an axial height of the cooling channel, so that a coolant flowing through the cooling channel is selectively accelerated and aligned on the one hand by the upward and downward movement of the piston and the constriction in the manner of a nozzle and on the other hand a relatively narrow flow cross-section limited equal directed flow in the sub-volume above and below the constriction is forced in each case in a roller-shaped flow.
  • This causes a much higher flow velocity of the engine oil commonly used as a coolant along the surface of the cooling channel.
  • the heat transfer between the metal and the relatively poorly heat-conducting oil is significantly improved, whereby the temperature of the piston can be significantly reduced.
  • the stabilization of the piston, in particular of the piston head by means of the ring carrier is particularly necessary when the piston of a Alloy, in particular made of aluminum or of an aluminum-containing material.
  • the constriction of the cooling channel to form the cross section according to the invention is arranged approximately centrally in the cooling channel.
  • the circumferential cooling channel which is a generally elongated, approximately in the axial direction, i. has parallel to the piston axis, extending cross-section, has a constriction about half the axial height of the cooling channel.
  • the cooling channel may be formed symmetrically in cross section, wherein a plane of symmetry or symmetry line or a point of symmetry in the region of the constriction of the cooling channel is arranged.
  • an axisymmetric cross section may be kidney-shaped, while a point symmetric cross section may be approximately dumbbell or octahedral.
  • the upper and lower sub-volumes are shaped so that an axially passing through the constriction coolant flow is received off-center and substantially tangentially in a dome-shaped fillet at the upper or lower end of the cooling channel.
  • the kinetic energy of the oil is used to a large extent for producing the inventively desired cylindrical movement in the upper or lower partial volume, which improves the heat transfer.
  • the oil jet could, after passing through the constriction, alternatively hit the end area in a central jet.
  • a central jet preferably in the upper and / or lower end region of the cooling channel in each case acting as a beam splitter circumferential rib present.
  • the rib preferably has a sharp, axially projecting circumferential edge, to which radially inwardly and outwardly each followed by a concave flank.
  • the cooling channel according to the invention can be formed only above, only below or on both sides with such a beam splitter.
  • the cooling channel according to the invention may also have an eg dumbbell-shaped cross section, which may be symmetrical to an axial and / or a radial axis.
  • the ring carrier is radially inwardly thicker, in particular to ensure a better or more stable arrangement of the ring carrier in the region of the ring part.
  • the decisive factor here is that an upper annular carrier wall in the axial direction and an axially lower annular carrier wall of the annular carrier extend in alignment with one another in cross-section, in order to allow better retention of the annular carrier in the piston body.
  • the ring carrier in cross section identifies an axial ring carrier height which increases radially inwards.
  • a preferred Ni-resist ring carrier has a smaller coefficient of thermal expansion than a typical piston material, such as e.g. an Al-Si alloy.
  • the radially inwardly widening ring carrier can therefore be supported on its flanks on the piston and is positively held in its groove.
  • Such a design of the ring carrier is particularly advantageous when the piston is poured.
  • the ring carrier can be used during or before the casting process in a corresponding mold. Accordingly, the ring carrier preferably has a cross-section which increases radially inward.
  • the cross-section of the ring carrier can be shaped like a quadrangle, for example trapezoidal, triangular or polygonal or the like.
  • the ring carrier is made of a nickel alloy, e.g. Ni resist is produced.
  • the ring carrier on the vorzutul made of light metal for example made of aluminum or an aluminum alloy piston ends occurring in the first annular groove reduce wear.
  • the piston is produced by a casting method, wherein the cooling channel is preferably formed by means of an insert in the piston.
  • the cooling channel could also be formed in a substantially annular casting which is attached to an otherwise forged piston. This means that the insert forming the cooling channel is inserted in a corresponding mold for the production of the piston or the casting and is then encapsulated with the material forming the piston.
  • the insert can be configured as a sand core or salt core, which is flushed out of the piston following the casting process.
  • the insert part for forming the cooling channel is preferably a sheet metal part which is welded or soldered to the ring carrier and forms the cooling channel between the two.
  • This has the advantage that the desired shape of the cooling channel can be realized by a simple forming of the designed as a sheet metal part insert.
  • the cross-sectional shape of the cooling channel with its substantially central constriction can be produced comparatively easily without having to use relatively fragile salt cores due to the desired shape.
  • the ring carrier forms, for example, a projecting into the cooling channel on the radially outer side protrusion. While a matching one Salt core from either axial direction could be placed on the ring carrier, a corresponding sheet metal part can be bent to fit after placing on the ring carrier.
  • the Fig. 1 shows a piston 1, which is produced by a casting process.
  • a mold 2 of the piston 1 is shown by means of a solid line, while a final shape 3 of the piston 1 by a dashed line is shown.
  • the casting mold 2 is machined or milled, for example by a turning process.
  • the piston 1 also has a ring carrier 4 and a cooling channel 5, which are previously welded or soldered as an insert 6 are realized and are accordingly introduced before casting the piston 1 in a corresponding mold and then with the piston 1 forming material, in particular Aluminum, to be poured.
  • the ring carrier 4 are preferably made of Ni resist and the cooling channel 5 made of austenitic steel / sheet.
  • the piston 1 also comprises a piston head 7 and a ring part 8 formed peripherally in the piston head 7.
  • a plurality of annular grooves 9 serving to receive piston rings are formed, one of these annular grooves 9 being formed in the radially outer region of the annular carrier 4 is.
  • the direction indicated by an arrow 18 radial direction is given with respect to an axial axis 10 of the piston 1 and extends correspondingly perpendicular thereto.
  • the cooling channel 5 is arranged in regions directly on the ring carrier 4, so that the ring carrier 4 forms a wall section 11 of the cooling channel 5. Accordingly, the ring carrier 4 and the cooling channel 5 are in direct contact, so that the cooling channel 5 on the one hand radially as far outside can be arranged as possible and also ensures improved cooling of the ring section 8.
  • the cooling channel 5 is formed such that it has a kidney-shaped cross-section.
  • the kidney-shaped cross-section is realized by means of a constriction 12 which lies in the region of approximately half of an axial height 13 of the cooling channel 5.
  • This shape of the cooling channel 5 is by means of a forming of the designed as a sheet metal part 14 insert 6 to form the Cooling channel 5 realized.
  • the kidney-shaped cooling channel 5 is formed substantially symmetrical, with a corresponding line of symmetry or plane of symmetry in the region of the constriction 12 of the cooling channel 5 extends.
  • the ratios of the dimensions of the cooling channel 5 should preferably be as follows: H ⁇ 2 B and b ⁇ 0 . 5 B
  • the first relationship allows a sufficiently large volume to hold the coolant, whereas the second relationship is important for the acceleration of the coolant, such as oil.
  • a cooling channel ceiling 21 of the cooling channel 5 is formed substantially dome-shaped or barrel-shaped.
  • the constriction 12 has in the embodiment shown according to Fig. 1 the same distance from the cooling channel bottom 22 and the cooling channel ceiling 21, whereby the coolant is forced in the region of the cooling channel ceiling 21 in a circular circumferential flow, as indicated by the circular arrows, so that the coolant several times per piston stroke with the wall of the cooling channel 5 in the region of a piston crown 16 and the piston recess 17 can interact. In this case, coolant of lower temperature is always accelerated by the constriction 12 and re-supplied.
  • the radial dimension B of the substantially dome-shaped cooling channel ceiling 21 at its widest point at least equal to twice the radial dimension b of the constriction 12, ie B ⁇ 2xb.
  • the formation of a cylindrical flow is promoted by the fact that the coolant of lower temperature off-center and preferably tangentially in the rounding of dome-shaped cooling duct ceiling occurs and is not significantly hindered by the already deflected by the cooling channel ceiling 21 and back flowing coolant in its flow.
  • the accelerated flow of oil through the constriction 12 leads to improved cooling of the ring carrier 4, to which also the increasing thickness of the ring carrier 4 contributes radially inward and thereby enlarged contact surface of the ring carrier 4 for the coolant.
  • the roller-shaped movement of the coolant increases the flow velocity of the oil, inter alia, along the dome-shaped cooling channel ceiling 21 and there improves the heat transfer and thereby the cooling of the piston crown 16 and the bowl rim or piston recess 17.
  • the piston 1 also has a piston stem 15, not shown in detail, which is arranged on the side projecting from a piston head 16 of the piston head 2 side of the piston head 2 and projects axially from the piston head 16.
  • the piston 1 comprises in the piston head 16 a piston recess 17.
  • Fig. 2 shows a further variant of the piston according to the invention 1.
  • the cooling channel 5 is in the in the Fig. 2 shown embodiment tilted in the radial direction.
  • a substantially axially directed flow in the region of the constriction 12 enters the dome-shaped cooling passage ceiling on the radially inner side, while it flows in the dome-shaped cooling passage bottom in the opposite direction on the radially outer side.
  • the cross section can thereby eg the shape of a slightly inclined "8" according to Fig. 2 exhibit.
  • the shape of the cooling channel can be adapted more precisely to the shape of the piston recess 17 and the heat transfer can be improved without having to deviate from an axial throughflow of the constriction 12.
  • the constriction 12 of both radial sides of the cooling channel 5 so that the corresponding wall portion 11 in contrast to the straight wall portion 11 of the in the Fig. 1 shown embodiment, curved and follows the course of a dumbbell or mecanicförmigen cross-section of the cooling channel 5.
  • the ring carrier 4 in cross section has a conical cross section with a radially inwardly increasing cross section.
  • an axially lower ring carrier wall 19 and an axially upper ring carrier wall 20 of the run Ring carrier 4 in cross section to each other and therefore not parallel in the examples shown, with the terms below and above refer to the illustration shown.
  • Such a design of the respective ring carrier 4 allows a better arrangement or a better grip of the ring carrier in the piston, in particular in a trained as Einlegteil 6 ring carrier. 4
  • ring carrier 4 shown a trapezoidal cross section, so that the wall portion 11, as mentioned, in cross section straight.
  • the Indian Fig. 2 ring carrier shown also has a trapezoidal cross-section, wherein the wall portion 11 has a shape adapted to the centrally narrowed shape of the cooling channel 5 shape.
  • the first relationship causes a sufficiently large space for receiving the coolant
  • the second relationship causes the required roll movement of the coolant, because even in the smaller of the two dome volumes, the tangentially entering flow of a deflected in the dome counterflow largely remains separate.
  • this is expressed by the minimum function.
  • B 1 B 2 . All in all, with such a Cooling channel geometry a particularly effective cooling of the piston 1 can be achieved.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Pistons, Piston Rings, And Cylinders (AREA)

Claims (9)

  1. Piston (1) pour un moteur à combustion interne, avec une tête de piston (7) et une tige de piston (15), dans lequel la tête de piston (7) présente une partie annulaire (8) périphérique ainsi que, dans la zone de la partie annulaire (8), un canal de refroidissement (5) périphérique et un support annulaire (4) périphérique,
    dans lequel le support annulaire (4) forme une section de paroi (11) du canal de refroidissement (5) et est ainsi en contact direct avec le canal de refroidissement (5), dans lequel le canal de refroidissement (5) présente une section transversale, qui présente, dans une zone centrale, un rétrécissement (12),
    caractérisé en ce
    - que la section transversale du canal de refroidissement (5) présente dans la direction axiale : une hauteur (H1), une première largeur radiale maximale (B1) dans une zone disposée sur le côté tourné vers le fond de piston du rétrécissement (12), une deuxième largeur radiale maximale (B2) dans une zone disposée sur le côté opposé au fond de piston du rétrécissement (12) et une troisième largeur radiale minimale (b) dans la zone du rétrécissement (12), où H 1 ≥ B 1 + B 2 et b ≤ 0.5 * min B 1 , B 2
    Figure imgb0008
    - que le support annulaire (4) présente une surface jouxtant le canal de refroidissement (5), avec une hauteur axiale (H2), dans lequel H 2 ≥ 0 , 5 * B 1 + B 2 .
    Figure imgb0009
  2. Piston selon la revendication 1,
    caractérisé en ce
    que le rétrécissement (12) se situe sur la moitié d'une hauteur axiale (13) du canal de refroidissement (5).
  3. Piston selon la revendication 1 ou 2,
    caractérisé en ce
    que la section transversale du canal de refroidissement (5) est réalisée avec une symétrie ponctuelle.
  4. Piston selon la revendication 1 ou 2,
    caractérisé en ce
    que la section transversale du canal de refroidissement (5) est réalisée avec une symétrie axiale par rapport à un axe radial.
  5. Piston selon l'une quelconque des revendications 1, 2 ou 4,
    caractérisé en ce
    que le rétrécissement (12) de la section transversale est formé par une partie faisant saillie périphérique, qui s'étend radialement vers l'extérieur depuis le côté intérieur du canal de refroidissement (5).
  6. Piston selon la revendication 5,
    caractérisé en ce
    que la section transversale du canal de refroidissement (5) est réalisée de manière à présenter la forme d'un haricot.
  7. Piston selon l'une quelconque des revendications 1 à 5,
    caractérisé en ce
    que le support annulaire (4) présente une section transversale s'agrandissant radialement vers l'intérieur.
  8. Piston selon l'une quelconque des revendications 1 à 6,
    caractérisé en ce
    que le piston (1) est fabriqué par un procédé de coulée, et le canal de refroidissement (5) est réalisé dans le piston (1) au moyen d'une partie d'insertion (6).
  9. Piston selon la revendication 8,
    caractérisé en ce
    que la partie d'insertion (6) est une pièce en tôle (14) fabriquée par un procédé de mise en forme.
EP13753156.2A 2012-08-31 2013-08-20 Piston Not-in-force EP2890883B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102012215541.4A DE102012215541A1 (de) 2012-08-31 2012-08-31 Kolben
PCT/EP2013/067302 WO2014033011A2 (fr) 2012-08-31 2013-08-20 Piston

Publications (2)

Publication Number Publication Date
EP2890883A2 EP2890883A2 (fr) 2015-07-08
EP2890883B1 true EP2890883B1 (fr) 2017-05-10

Family

ID=49035570

Family Applications (1)

Application Number Title Priority Date Filing Date
EP13753156.2A Not-in-force EP2890883B1 (fr) 2012-08-31 2013-08-20 Piston

Country Status (7)

Country Link
US (1) US9664137B2 (fr)
EP (1) EP2890883B1 (fr)
JP (1) JP6340368B2 (fr)
CN (1) CN104603438B (fr)
BR (1) BR112015004142A8 (fr)
DE (1) DE102012215541A1 (fr)
WO (1) WO2014033011A2 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10294887B2 (en) 2015-11-18 2019-05-21 Tenneco Inc. Piston providing for reduced heat loss using cooling media
EP4256193A2 (fr) * 2020-12-03 2023-10-11 Cummins, Inc. Piston, ensemble bloc et procédé de refroidissement

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* Cited by examiner, † Cited by third party
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JPH07180605A (ja) * 1993-12-22 1995-07-18 Yanmar Diesel Engine Co Ltd ピストンおよびその製造方法
JPH10184450A (ja) * 1996-12-26 1998-07-14 Isuzu Motors Ltd 冷却空洞部を持つピストンとその製造方法
JPH1182738A (ja) * 1997-09-16 1999-03-26 Hino Motors Ltd ピストン用冷却空洞付き耐摩環及びその製造方法
AT3210U1 (de) 1998-12-10 1999-11-25 Avl List Gmbh Kolben für eine brennkraftmaschine
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DE10134293B4 (de) 2001-07-14 2009-06-04 Mahle Gmbh Gekühlter Ringträger für einen Kolben
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DE10352244A1 (de) * 2003-11-08 2005-06-09 Mahle Gmbh Verfahren zur Herstellung eines Kolbens für einen Verbrennungsmotor
JP4838858B2 (ja) * 2005-12-17 2011-12-14 マーレ インターナショナル ゲゼルシャフト ミット ベシュレンクテル ハフツング 内燃機関用の２部分から成るピストン
DE102005061059A1 (de) * 2005-12-21 2007-06-28 Mahle International Gmbh Kolben für einen Verbrennungsmotor
DE102005061074A1 (de) 2005-12-21 2007-06-28 Mahle International Gmbh Kolben für einen Verbrennungsmotor und Verfahren zu seiner Herstellung
DE102006013884A1 (de) 2006-03-25 2007-09-27 Mahle International Gmbh Kolben für einen Verbrennungsmotor
JP2007263068A (ja) * 2006-03-29 2007-10-11 Toyota Motor Corp ピストン耐摩環
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JP2009215978A (ja) * 2008-03-11 2009-09-24 Honda Motor Co Ltd 燃料直噴エンジン
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DE102008062219A1 (de) * 2008-12-13 2010-06-17 Mahle International Gmbh Kolben für einen Verbrennungsmotor
US20130000482A1 (en) * 2010-10-22 2013-01-03 GM Global Technology Operations LLC Sand Casting An Aluminum Diesel Piston With An As-Cast, Reentrant Combustion Bowl For Light Or Medium Duty Diesel Engines
DE102010056220A1 (de) * 2010-12-24 2012-06-28 Mahle International Gmbh Kolben für einen Verbrennungsmotor
DE102011103105A1 (de) * 2011-05-25 2012-11-29 Mahle International Gmbh Kolben für einen Verbrennungsmotor und Verfahren zur Herstellung des Kolbens
DE102011116332A1 (de) * 2011-07-05 2013-01-10 Mahle International Gmbh Kolben für einen Verbrennungsmotor

Also Published As

Publication number Publication date
JP6340368B2 (ja) 2018-06-06
CN104603438B (zh) 2018-07-31
US9664137B2 (en) 2017-05-30
CN104603438A (zh) 2015-05-06
WO2014033011A2 (fr) 2014-03-06
BR112015004142A8 (pt) 2019-08-06
EP2890883A2 (fr) 2015-07-08
WO2014033011A3 (fr) 2014-05-01
JP2015528537A (ja) 2015-09-28
BR112015004142A2 (pt) 2017-07-04
DE102012215541A1 (de) 2014-03-06
US20150322886A1 (en) 2015-11-12

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