EP3004611A1 - Piston pour moteur à combustion interne - Google Patents

Piston pour moteur à combustion interne

Info

Publication number
EP3004611A1
EP3004611A1 EP14753002.6A EP14753002A EP3004611A1 EP 3004611 A1 EP3004611 A1 EP 3004611A1 EP 14753002 A EP14753002 A EP 14753002A EP 3004611 A1 EP3004611 A1 EP 3004611A1
Authority
EP
European Patent Office
Prior art keywords
piston
cooling channel
piston head
head
piston according
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.)
Withdrawn
Application number
EP14753002.6A
Other languages
German (de)
English (en)
Inventor
Rainer Scharp
Peter Kemnitz
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 EP3004611A1 publication Critical patent/EP3004611A1/fr
Withdrawn legal-status Critical Current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 
    • F02F3/16—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
    • 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
    • F02F3/18—Pistons  having cooling means the means being a liquid or solid coolant, e.g. sodium, in a closed chamber in piston

Definitions

  • the present invention relates to a piston for an internal combustion engine, having a piston head and a piston skirt, wherein the piston head has a piston crown, a circumferential land land, a circumferential ring part with annular grooves and in the region of the ring part a circumferential closed cooling channel with a cooling channel bottom and a cooling duct ceiling.
  • the object of the present invention is to further develop a generic piston so that an optimized heat dissipation takes place from the piston head during engine operation.
  • the solution is that the cooling channel bottom is arranged above the lowermost annular groove.
  • the cooling channel in the axial direction usually extends to the level of the lowest annular groove and below, in order to achieve with the aid of the largest possible cooling channel sufficient cooling, especially of steel pistons in engine operation. Due to the shaker effect, the cooling oil moves between the cooling duct ceiling, i. a very hot area, and the cooling channel bottom, i. a comparatively cool area, back and forth. Due to the significantly lower temperatures in the region of the cooling channel bottom, practically no heat absorption from the piston head into the cooling oil takes place there. It also takes place due
  • CONFIRMATION COPY the low thermal gradient in the direction of the ring part and piston shaft only a comparatively low heat dissipation from the cooling oil instead.
  • the piston according to the invention is distinguished by the fact that the cooling channel is shortened in the axial direction compared to the prior art. This has the consequence that the cooling oil in particular in the region of the cooling channel bottom in greater proximity to the highly heat-loaded cooling channel bottom and thus moves in total in hotter areas than is the case in the prior art. Therefore, in each phase of the piston movement takes place heat absorption from the hot areas of the piston head into the cooling oil. In particular, if the amount of cooling oil known from the prior art is maintained and the cooling oil supply is set up so that the cooling oil is rapidly exchanged during engine operation, a significantly improved cooling of the piston head results in comparison with the prior art.
  • the cooling channel bottom between the first annular groove and the second annular groove is arranged to further increase the cooling power by the cooling oil moves in engine operation in even greater proximity to the hot piston bottom.
  • an at least partially circumferential recess is introduced into the piston head in the piston head below the cooling channel bottom.
  • a further preferred embodiment provides that the height of the top land is at most 9% of the nominal diameter of the piston head. This causes a particularly advantageous for heat dissipation positioning of the cooling channel with respect to the piston crown and the ring section.
  • the distance between the piston crown and the bottom of the cooling channel can be between 11% and 17% of the nominal diameter of the piston head.
  • the height of the cooling channel can be 0.8 times to 1.7 be fold of its width.
  • the distance between the piston head and the cooling channel ceiling can be between 3% and 7% of the nominal diameter of the piston head.
  • the compression height may, for example, be between 38% and 45% of the nominal diameter of the piston head.
  • a combustion bowl is formed in the piston head and that the smallest wall thickness in the radial direction between the combustion bowl and the cooling channel is between 2.5% and 4.5% of the nominal diameter of the piston head.
  • the combustion bowl may, for example, be provided with an undercut in order to determine the wall thickness between the combustion bowl and the cooling channel.
  • the recess below the cooling channel bottom preferably has a U-shaped or oval cross section in order to avoid the formation of sharp edges and thus to minimize the risk of mechanical stresses in the material.
  • the piston according to the invention may be formed as a one-piece piston, or it may, for example, be composed of at least two non-detachably interconnected components.
  • the piston according to the invention can have a piston main body and a circumferential bowl edge reinforcement.
  • the piston according to the invention may, for example, also have a piston main body and a revolving piston bottom element.
  • the present invention is particularly suitable for pistons of at least one steel material. Embodiments of the present invention are explained in more detail below with reference to the accompanying drawings. In a schematic, not to scale representation:
  • Figure 1 shows a first embodiment of a piston according to the invention in section
  • Figure 2 is an overall view of two further embodiments of the piston according to the invention in section;
  • FIG. 3 is an enlarged partial view of the cooling channel and the ring section according to Figures 1 and 2;
  • FIG. 1 Figures a schematic representation of the cooling oil movement in a piston 4a, 4b according to the present invention
  • FIG. 1 Figures a schematic representation of the cooling oil movement in a piston 5a, 5b according to the prior art.
  • Figure 1 shows a first embodiment of a piston 10 according to the invention.
  • the piston 10 is in the embodiment of a one-piece, cast in a conventional manner with the aid of a salt core piston.
  • the piston 10 is made in the embodiment of a steel material.
  • the piston 10 has a piston head 11 with a combustion bowl 13 having a piston head 12, a peripheral land 14 and a ring portion 15 with annular grooves 16, 17, 18 for receiving piston rings (not shown). In the amount of the ring section 15, a circumferential closed cooling channel 19 is provided.
  • the piston 10 further includes a piston shaft 21 with piston bosses 22 and hub bores 23 for receiving a piston pin (not shown).
  • the Kol hub 22 are connected via hub connections 24 with the underside of the piston head 11.
  • the piston hubs 22 are connected to each other via running surfaces 25.
  • the cooling channel 19 has a cooling channel bottom 26 and a cooling channel cover 27.
  • the cooling channel bottom 26 is arranged approximately between the first annular groove 16 and the second annular groove 17.
  • an at least partially circumferential recess 28 is introduced into the piston head 11 in the exemplary embodiment.
  • the recess 28 has an approximately U-shaped cross-section in the exemplary embodiment.
  • the recess 28 can be incorporated by a forging process in the piston head 11.
  • the recess 28 is provided only above the running surfaces 25 of the piston 10, because the forging tool above the piston boss 22 has too little room for maneuver.
  • the compression height KH is in the embodiment between 38% and 45% of the nominal diameter DN of the piston head eleventh
  • FIG. 2 shows, in a representation rotated by 90 ° with respect to FIG. 1, an overall view of second further exemplary embodiments of pistons 110, 210 according to the invention.
  • the representations of the respective exemplary embodiments are separated by the center line M.
  • the pistons 110, 210 are constructed in a similar manner as the piston 10 according to FIG. 1. Therefore, matching structural elements are provided with the same reference numerals, and reference is made in this regard to the description relating to FIG.
  • the pistons 110, 210 are each composed of two non-detachably interconnected components.
  • the piston 110 (illustration left of the center line M) consists of a piston body 131 and a circumferential bowl edge reinforcement 132.
  • the trough edge reinforcement comprises in the exemplary embodiment, the trough edge of the combustion bowl 13 and a part of the piston crown 12.
  • the trough edge reinforcement 132 can in particular by a welding process, for example. Electron beam welding or laser welding, be connected to the piston body 131.
  • the piston 210 (illustration on the right of the center line M) consists of a piston main body 231 and a circumferential piston bottom element 232.
  • the piston bottom element 232 in the exemplary embodiment comprises the trough edge of the combustion trough 13, the piston head 12, the top land 14 and the uppermost annular groove 16.
  • the piston bottom element 232 can In particular by a welding process, for example. Friction welding, electron beam welding or laser welding, be connected to the piston body 231.
  • FIG. 3 shows, in an enlarged partial view, the cooling channel 19 and the piston bottom 12, a part of the combustion bowl 13 the top land 14, the ring part 15 with the annular grooves 16, 17, 18 of the piston according to the invention and the recess 28 according to FIGS. 1 and 2.
  • the combustion bowl 13 is provided with an undercut 29 to determine the wall thickness between the combustion bowl 13 and the cooling channel 19 (see below).
  • the height h of the top land 14 is at most 9% of the nominal diameter DN of the piston head 11 (see FIGS. 1 and 2).
  • a particularly advantageous for the heat dissipation positioning of the cooling channel 19 with respect to the piston head 12 and the ring section 15 is effected.
  • the distance a between the piston head 12 and the cooling channel bottom 26 is between 11% and 17% of the nominal diameter DN of the piston head 11 (see FIGS. 1 and 2).
  • the cooling channel 19 is in optimal proximity to the hot Piston bottom 12 and positioned in an optimal position relative to the cooler annular grooves 16, 17, 18.
  • the height c of the cooling passage 19 is 0.8 times to 1.7 times its width d. This design rule causes an optimal volume of the cooling channel 19 and an optimal orientation relative to the hot combustion bowl 13, in particular to the bowl rim, and the hot piston bottom 12 and the cooler annular grooves 16, 17, 18th
  • the distance b between the piston head 12 and the cooling channel cover 27 is between 3% and 7% of the nominal diameter DN of the piston head 11 (compare FIGS. 1 and 2). This design rule also causes optimal positioning of the cooling channel 19 with respect to the hot piston bottom 12.
  • the smallest wall thickness w in the radial direction between the combustion bowl 13 and the cooling channel 19 is between 2.5% and 4.5% of the nominal diameter DN of the piston head 11. For an improved heat transfer between the combustion bowl 13 and the cooling channel 19 is achieved.
  • Figures 4a and 4b and 5a and 5b show schematically the cooling oil movement during engine operation and the temperature zones in the region of the combustion bowl, the piston head, the cooling channel and the annular grooves both for a piston according to the invention ( Figures 4a and 4b) and for a piston according to the state the technique ( Figures 5a and 5b).
  • FIGS. 4 a, 4 b, 5 a, 5 b schematically indicate three heat zones, namely “hot”, “warm” and “cool.” This is intended to illustrate the relative temperature differences in the individual piston areas.
  • the cooling channel is compared to the prior art in the axial direction is shortened. This has the consequence that the cooling oil is moved almost exclusively along the "hot” areas of the piston crown and the combustion bowl, so that heat absorption from the "hot” regions of the piston head into the cooling oil takes place in each phase of the piston movement.
  • the known from the prior art amount of cooling oil should be maintained and the engine management be set up so that the cooling oil is quickly replaced during engine operation.
  • the cooling channel generally extends in the axial direction to the level of the lowest annular groove and below in order to achieve sufficient cooling during engine operation with the aid of the largest possible cooling channel. Due to the shaker effect, the cooling oil moves between a "hot” area, namely the piston crown and the bowl rim of the combustion bowl and a "cool” area, namely the cooling channel bottom. Due to the significantly lower temperatures in the region of the cooling channel bottom, practically no heat absorption from the piston head into the cooling oil takes place there.
  • the piston according to the invention has a significantly improved cooling of the piston head compared to the prior art.

Landscapes

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

Abstract

L'invention concerne un piston (10, 110, 210) pour un moteur à combustion interne, comprenant une tête de piston (11) et une jupe de piston (21), la tête de piston (11) comprenant un fond de piston (12), un cordon de feu périphérique (14), une partie annulaire (15) périphérique présentant des gorges annulaires (16, 17, 18) et, dans la zone de la partie annulaire (15), un canal de refroidissement (19) périphérique fermé comprenant un fond de canal (26) et une couverture de canal (27). Selon l'invention, un évidement (28) périphérique est ménagé dans la tête de piston (11) sous le fond de canal (26) de sorte que le fond de canal (26) se situe au-dessus de la gorge annulaire (18) la plus basse.
EP14753002.6A 2013-05-31 2014-05-28 Piston pour moteur à combustion interne Withdrawn EP3004611A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102013009155.1A DE102013009155A1 (de) 2013-05-31 2013-05-31 Kolben für einen Verbrennungsmotor
PCT/DE2014/000265 WO2014190964A1 (fr) 2013-05-31 2014-05-28 Piston pour moteur à combustion interne

Publications (1)

Publication Number Publication Date
EP3004611A1 true EP3004611A1 (fr) 2016-04-13

Family

ID=51383522

Family Applications (1)

Application Number Title Priority Date Filing Date
EP14753002.6A Withdrawn EP3004611A1 (fr) 2013-05-31 2014-05-28 Piston pour moteur à combustion interne

Country Status (7)

Country Link
US (1) US10174712B2 (fr)
EP (1) EP3004611A1 (fr)
JP (1) JP2016521815A (fr)
CN (1) CN105392981B (fr)
BR (1) BR112015029766A2 (fr)
DE (1) DE102013009155A1 (fr)
WO (1) WO2014190964A1 (fr)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102016201628A1 (de) * 2016-02-03 2017-08-03 Federal-Mogul Nürnberg GmbH Kolben aus Stahl- oder Grauguss für einen Verbrennungsmotor und Verfahren zur Herstellung eines Kolbens durch Stahl- oder Grauguss
US10690247B2 (en) * 2017-01-10 2020-06-23 Tenneco Inc. Galleryless short compression insulated steel piston
CN109162823A (zh) * 2018-11-09 2019-01-08 广西玉柴机器股份有限公司 柴油机的降重钢活塞
DE102019204559A1 (de) * 2019-04-01 2020-10-01 Federal-Mogul Nürnberg GmbH Kolben für einen Verbrennungsmotor
CN111535936A (zh) * 2020-06-29 2020-08-14 安徽江淮汽车集团股份有限公司 一种发动机活塞

Citations (3)

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US4428330A (en) * 1982-09-08 1984-01-31 Kabushiki Kaisha Komatsu Seisakusho Piston for internal combustion engines
DE10007851A1 (de) * 2000-02-21 2001-08-23 Ks Kolbenschmidt Gmbh Leichtmetallkolben
US20120037112A1 (en) * 2009-11-06 2012-02-16 Florin Muscas Steel piston with cooling gallery and method of construction thereof

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DE4014705C2 (de) 1990-05-08 1999-06-10 Mahle Gmbh Gekühlter Tauchkolben für Verbrennungsmotoren mit voneinander getrenntem Kolbenoberteil und Kolbenschaft
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DE10063568A1 (de) 2000-12-20 2002-07-04 Mahle Gmbh Kühlkanalkolben für einen Dieselmotor mit Direkteinspritzung mit einem Kolbendurchmesser von 100 mm
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US8544441B2 (en) 2011-08-04 2013-10-01 Federal-Mogul Ignition Company Piston including a pair of cooling chambers
US10753310B2 (en) * 2012-02-10 2020-08-25 Tenneco Inc. Piston with enhanced cooling gallery
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US4428330A (en) * 1982-09-08 1984-01-31 Kabushiki Kaisha Komatsu Seisakusho Piston for internal combustion engines
DE10007851A1 (de) * 2000-02-21 2001-08-23 Ks Kolbenschmidt Gmbh Leichtmetallkolben
US20120037112A1 (en) * 2009-11-06 2012-02-16 Florin Muscas Steel piston with cooling gallery and method of construction thereof

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Title
See also references of WO2014190964A1 *

Also Published As

Publication number Publication date
JP2016521815A (ja) 2016-07-25
DE102013009155A1 (de) 2014-12-04
US20160123273A1 (en) 2016-05-05
BR112015029766A2 (pt) 2017-07-25
CN105392981A (zh) 2016-03-09
US10174712B2 (en) 2019-01-08
CN105392981B (zh) 2019-04-09
WO2014190964A1 (fr) 2014-12-04

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