EP2729689A1 - Piston pour un moteur à combustion interne - Google Patents

Piston pour un moteur à combustion interne

Info

Publication number
EP2729689A1
EP2729689A1 EP12755778.3A EP12755778A EP2729689A1 EP 2729689 A1 EP2729689 A1 EP 2729689A1 EP 12755778 A EP12755778 A EP 12755778A EP 2729689 A1 EP2729689 A1 EP 2729689A1
Authority
EP
European Patent Office
Prior art keywords
cooling channel
piston
constriction
piston according
ceiling
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.)
Granted
Application number
EP12755778.3A
Other languages
German (de)
English (en)
Other versions
EP2729689B1 (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 EP2729689A1 publication Critical patent/EP2729689A1/fr
Application granted granted Critical
Publication of EP2729689B1 publication Critical patent/EP2729689B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P3/00—Liquid cooling
    • F01P3/06—Arrangements for cooling pistons
    • F01P3/10—Cooling by flow of coolant through 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 
    • F02F3/16—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 having a piston head and a piston skirt, wherein the piston head has a circumferential annular portion and in the region of the annular part a circumferential cooling channel and the piston shaft each having a pressure side and a counter-pressure associated tread.
  • the object of the present invention is to further develop a generic piston so that the cooling in the region of the piston crown is further improved.
  • the solution is that the cooling channel has a constriction.
  • the present invention is based on the continuity equation of the fluid dynamics, according to which a narrowing of the flow cross-section leads to an increase of the flow velocity with flowing fluids.
  • the constriction provided according to the invention in cooperation with the shaker effect, causes the coolant circulating in the cooling channel not only to be mixed, but also specifically accelerated by the constriction and guided in the direction of the piston crown. This causes the mixed and thus cooled coolant is passed much more efficiently and more frequently per piston stroke than in the previously known piston on the particularly hot wall sections of the cooling channel in the region of the piston crown.
  • the inventively provided constriction has a distance from the cooling channel bottom, which corresponds to at least one third of the axial height and / or at most two thirds of the axial height of the cooling channel.
  • a particularly effective acceleration of the coolant flow in the direction of the cooling duct ceiling can be achieved.
  • the constriction preferably has substantially the same distance from the cooling channel bottom and from the cooling channel ceiling.
  • constriction is expediently designed as a circumferential constriction in order to bring about the acceleration effect along the entire cooling channel.
  • a preferred embodiment provides that the constriction is formed by exactly one increase in material on a cooling passage wall, and that the cooling passage ceiling is formed substantially dome-shaped. This ensures that the coolant is forced in the region of the cooling duct ceiling in a circular circulating flow, so that interacts with the wall of the cooling channel several times per piston stroke. In this case, coolant of lower temperature is always accelerated and replenished by the constriction. This effect is particularly effective when the radial dimension of the substantially dome-shaped cooling duct ceiling at its widest point is at least equal to twice the radial extent of the constriction. In this case, less hot coolant may flow downwardly so that the flow of lower temperature coolant through the throat toward the cooling gallery ceiling is not significantly hindered.
  • a further preferred embodiment of the present invention is that the constriction is formed by exactly two opposing increases in material on two cooling channel walls. This refinement is particularly particular in multi-piece friction welded pistons when the weld passes through the cooling channel, so that the Sch undulste form the opposing material increases, which cause the constriction.
  • the cooling channel ceiling has a flow divider in its zenith, which is arranged centrally to the constriction.
  • the coolant flowing through the constriction accelerated in the region of the cooling duct ceiling is forced into two oppositely rotating flows which can interact with the wall of the cooling passage several times per piston stroke.
  • coolant of lower temperature is always accelerated and replenished by the constriction.
  • This effect is particularly effective when the radial dimension of the cooling duct ceiling at its widest point is at least equal to twice the radial extent of the constriction. In this case, less hot coolant may flow down so that the flow of lower temperature coolant through the restriction is not significantly impeded.
  • the areas of the cooling duct ceiling, which adjoin the flow divider may be arcuate or circular in cross-section. Further, it is particularly useful to form the flow divider in cross-section V-shaped or conical.
  • the cooling channel wall adjacent to the ring section may be designed to be inclined perpendicularly or obliquely inwards.
  • a further preferred embodiment of the present invention is that the constriction is formed by exactly two axially offset from each other material increases on two cooling channel walls.
  • This refinement leads to an outer expansion adjacent to the ring section and / or to the top land in the area of the cooling channel ceiling and, in the region of the cooling channel bottom, to a center of the piston bottom oriented, in particular to an optionally present connection. combustion cavity adjacent, inner expansion is formed.
  • the cooling effect can, for example, be influenced by the fact that the two material elevations have a different thickness, so that the two extensions are formed with radii of different sizes.
  • the expansion with the larger radius can then be arranged in the region of the largest thermal load of the piston head.
  • the present invention is suitable for all piston types and all piston types and can be realized with any piston material.
  • Figure 1 shows a first embodiment of a piston according to the invention in a partial view in section
  • Figure 2 shows another embodiment of a piston according to the invention in a perspective partial view in section
  • Figure 3 shows another embodiment of a piston according to the invention in a partial view in section.
  • FIG. 1 shows a first embodiment of a piston 10 according to the invention.
  • the piston 10 may be a one-piece or multi-piece piston.
  • the piston 10 may be made of a steel material and / or a light metal material.
  • FIG. 1 shows, by way of example, a one-part piston head 11 of a piston 10 according to the invention.
  • the piston head 11 has a piston crown 12, which has a combustion bowl 13, a circumferential top land 14 and a piston head 11 Ring section 15 for receiving piston rings (not shown).
  • a circumferential cooling channel 16 is provided with a cooling channel bottom 17 and a cooling channel ceiling 18.
  • the piston 10 also has, in a known manner, a piston shaft, which may be formed integrally with the piston head 11 or as a separate component that is fixedly connected to the piston head 11 in a manner known per se or, for example, in the manner of a pendulum piston (not shown) ).
  • the cooling channel 16 has a circumferential constriction 20.
  • the constriction 20 is formed in this embodiment by exactly one increase in material 21 in the combustion bowl 13 adjacent cooling channel wall.
  • the cooling duct wall 22 adjacent to the ring section 15 is substantially vertical in this exemplary embodiment. It can also be slightly inclined inwards, i. in the direction of the combustion bowl 13, be formed inclined.
  • the cooling channel ceiling 18 of the cooling channel 16 is substantially dome-shaped.
  • the constriction 20 has in this embodiment at its narrowest point substantially the same distance A from the cooling channel bottom 17 and from the cooling channel ceiling 18.
  • the coolant is forced in the region of the cooling channel ceiling 18 in a circular circulating flow, as indicated by the circular arrows, so that the coolant can interact with the wall of the cooling channel in the region of the piston head 12 and the combustion bowl 13 several times per piston stroke.
  • coolant of lower temperature is always accelerated by the constriction 20 and re-supplied.
  • the radial dimension B of the substantially dome-shaped cooling channel ceiling 18 at its widest point at least equal to twice the radial dimension b of the constriction 20, ie B> 2xb.
  • less hot coolant may flow down so that the flow of lower temperature coolant through the throat 20 is not significantly impeded toward the cooling channel ceiling 18.
  • the piston 10 according to the invention or the piston upper part 11 can be produced in a manner known per se by casting, forging, sintering, etc.
  • the inventively designed cooling channel can be prepared in a conventional manner by casting with a salt core.
  • Figure 2 shows another embodiment of a piston 110 according to the invention.
  • the piston 110 may be a one-piece or multi-piece piston.
  • the piston 110 may be a one-piece or multi-piece piston.
  • FIG. 2 shows by way of example a one-part piston head 111 of a piston 110 according to the invention.
  • the piston head 111 has a piston bottom 112 having a combustion bowl 113, a circumferential top land
  • a circumferential cooling channel 116 is provided with a cooling channel bottom 117 and a cooling channel ceiling 118.
  • the piston 110 also has, in a manner known per se, a piston shaft which is connected to the piston head
  • piston head 111 be integrally formed or as a separate component that with the piston head 111 in a conventional manner fixed or, for example, in the manner of a pendulum piston connected (not shown).
  • the cooling channel 116 has a circumferential restriction 120.
  • the constriction 120 is formed in this embodiment by exactly two opposing material increases 121 in the two adjacent to the combustion bowl 113 and the ring section 115 cooling channel walls.
  • the cooling channel ceiling 118 of the cooling channel 116 has in this embodiment in its zenith a flow divider 123, which is arranged centrally to the constriction 120.
  • the distance between the constriction 120 and the cooling channel bottom 117 in this exemplary embodiment is approximately the same as the distance between the constriction 120 and the cooling channel ceiling 118.
  • the radial dimension B of the cooling channel ceiling 118 at its widest point at least equal to twice the radial dimension b of the constriction 120, ie B> 2xb. In this case, less hot coolant may flow downwardly so that the flow of lower temperature coolant through the restriction 120 toward the cooling gallery deck 118 is not significantly impeded.
  • the areas 118a, 118b of the cooling duct ceiling 118, which connect to the flow divider 123, in cross-section arcuate or circular and the flow divider 123 in cross-section V-shaped.
  • the piston 110 according to the invention or the piston upper part 111 can be produced in a manner known per se by casting, forging, sintering, etc.
  • the cooling channel 116 designed according to the invention can be produced in a manner known per se by casting with a salt core.
  • FIG. 3 shows a further exemplary embodiment of a piston 210 according to the invention.
  • the piston 210 may be a one-part or multi-part piston.
  • the piston 210 may be made of a steel material and / or a light metal material.
  • FIG. 3 shows by way of example a one-piece piston head 211 of an inventive To the piston according to the invention 210.
  • the piston head 211 has a with a combustion bowl 213 having a piston head 212, a peripheral land 214 and a ring portion 215 for receiving piston rings (not shown).
  • a circumferential cooling channel 216 is provided with a cooling channel bottom 217 and a cooling channel ceiling 218.
  • the piston 210 also has, in a manner known per se, a piston shaft which may be formed integrally with the piston head 211 or as a separate component that is fixedly connected to the piston head 211 in a manner known per se or, for example, in the manner of a pendulum piston (not shown) ).
  • the cooling channel 216 has a circumferential restriction 220.
  • the constriction 220 is formed in this embodiment by exactly two axially offset from each other material increases 221a, 221b in the two adjacent to the combustion bowl 213 and the ring section 215 cooling channel walls.
  • an inner extension 224 extending to the combustion recess 213 is formed in the region of the cooling channel bottom 217.
  • an outer extension 225 extending to the uppermost annular groove of the annular portion 215 and to the land land 214 is formed.
  • these regions of the piston head 211 which are subject to particularly high thermal loads, namely the piston head 212 in the region of the combustion bowl 213 and the land land 214, are cooled very effectively during engine operation.
  • This cooling effect is also influenced in this embodiment in that the material increase 221a has a thickness D1 that is greater than the thickness D2 of the material increase 221b. Consequently, the inner extension 224 has a larger radius on the outer extension 225.
  • the region of the combustion bowl is particularly effectively cooled.
  • the material increase 221b may have a greater thickness than the material increase 221a, so that in this case the outer extension 225 has a larger radius than the inner extension 224 and consequently the area of the piston crown 213 and the land 214 is cooled particularly effectively (not shown).
  • the expansions 224, 225 may extend as far as possible in the radial direction inwards or outwards, as indicated by dash-dotted lines in FIG.
  • the cooling channel bottom 217 and the cooling channel cover 218 of the cooling channel 216 are substantially dome-shaped.
  • the constriction 220 has at its narrowest point substantially the same distance A from the cooling channel bottom 217 and from the cooling channel ceiling 218.
  • the coolant in the region of the cooling channel bottom 217 and in the region of the cooling channel cover 218 is forced into a counterclockwise circular flow, as indicated by the circular arrows.
  • the coolant can interact several times per piston stroke with the wall of the cooling channel in the region of the piston head 212 and the combustion bowl 213. In this case, coolant of lower temperature is always accelerated by the constriction 220 and re-supplied.
  • the radial dimension B of the inner widening 224 or the outer widening 225 at their respective widest points is at least twice the radial dimension b of the constriction 20, ie B> 2xb, as shown in FIG the outer widening 225 is shown.
  • less hot coolant may flow down so that the flow of lower temperature coolant through the throat 220 does not substantially obstruct the direction of the cooling gallery ceiling 218 and the area of the piston head 212 is effectively cooled.
  • the piston 210 according to the invention or the piston upper part 211 can be produced in a manner known per se by casting, forging, sintering, etc.
  • an integral piston upper part 211 as shown in FIG. 3, the invented According to the design designed cooling channel 216 are prepared in a conventional manner by casting with a salt core.

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

La présente invention concerne un piston (10, 110, 210) pour un moteur à combustion interne, comprenant une tête de piston (11, 111, 211) et une jupe de piston, la tête de piston (11, 111, 211) présentant une partie annulaire périphérique (15, 115, 215) et, dans la région de cette partie annulaire (15, 115, 215), un canal de refroidissement périphérique (16, 116, 216) comportant un fond (17, 117, 217) et une partie supérieure (18, 118, 218). Selon l'invention, le canal de refroidissement (16, 116, 216) présente un rétrécissement (20, 120, 220).
EP12755778.3A 2011-07-05 2012-07-04 Piston pour un moteur à combustion interne Active EP2729689B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102011106562 2011-07-05
DE102011116332A DE102011116332A1 (de) 2011-07-05 2011-10-19 Kolben für einen Verbrennungsmotor
PCT/DE2012/000670 WO2013004215A1 (fr) 2011-07-05 2012-07-04 Piston pour un moteur à combustion interne

Publications (2)

Publication Number Publication Date
EP2729689A1 true EP2729689A1 (fr) 2014-05-14
EP2729689B1 EP2729689B1 (fr) 2024-04-17

Family

ID=47426675

Family Applications (1)

Application Number Title Priority Date Filing Date
EP12755778.3A Active EP2729689B1 (fr) 2011-07-05 2012-07-04 Piston pour un moteur à combustion interne

Country Status (8)

Country Link
US (1) US9109530B2 (fr)
EP (1) EP2729689B1 (fr)
JP (1) JP6335781B2 (fr)
KR (1) KR101962988B1 (fr)
CN (1) CN103649509B (fr)
BR (1) BR112014000079B1 (fr)
DE (1) DE102011116332A1 (fr)
WO (1) WO2013004215A1 (fr)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102012014192A1 (de) 2012-07-18 2014-01-23 Mahle International Gmbh Kolben für einen Verbrennungsmotor
DE102012215541A1 (de) 2012-08-31 2014-03-06 Mahle International Gmbh Kolben
JP6209382B2 (ja) * 2013-07-24 2017-10-04 日立オートモティブシステムズ株式会社 内燃機関のピストンと該ピストン製造方法及び製造装置
WO2017150321A1 (fr) * 2016-03-02 2017-09-08 本田技研工業株式会社 Piston de moteur à combustion interne et son procédé de fabrication
DE102016224280A1 (de) * 2016-06-02 2017-12-07 Mahle International Gmbh Kolben einer Brennkraftmaschine
DE102019213953A1 (de) * 2019-09-12 2021-03-18 Mahle International Gmbh Kolben für eine Brennkraftmaschine
DE102019219614A1 (de) * 2019-12-13 2021-06-17 Mahle International Gmbh Kolben für eine Brennkraftmaschine
US11326549B2 (en) * 2020-01-21 2022-05-10 Ford Global Technologies, Llc 218-0266 volcano-shaped inlet of piston oil-cooling gallery
DE102020207512A1 (de) 2020-06-17 2021-12-23 Mahle International Gmbh Verfahren zur Herstellung eines Kolbens
CN114278455B (zh) * 2020-09-27 2023-12-19 马勒汽车技术（中国）有限公司 具有分流式内冷流道的活塞
US12163484B2 (en) * 2020-12-03 2024-12-10 Cummins Inc. Piston, block assembly, and method for cooling
DE102021203241A1 (de) 2021-03-30 2022-10-06 Mahle International Gmbh Kolben für eine Brennkraftmaschine und Verfahren zur Herstellung des Kolbens
DE102021211034A1 (de) 2021-09-30 2023-03-30 Mahle International Gmbh Kolben
CN117028055A (zh) * 2023-07-31 2023-11-10 滨州渤海活塞有限公司 钢活塞冷却腔体结构及钢活塞

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US8671905B2 (en) * 2011-07-12 2014-03-18 Mahle International Gmbh Piston for an internal combustion engine and method for its production

Also Published As

Publication number Publication date
JP6335781B2 (ja) 2018-05-30
JP2014520991A (ja) 2014-08-25
CN103649509B (zh) 2019-10-15
BR112014000079B1 (pt) 2021-08-03
EP2729689B1 (fr) 2024-04-17
KR20140050020A (ko) 2014-04-28
KR101962988B1 (ko) 2019-03-27
DE102011116332A1 (de) 2013-01-10
CN103649509A (zh) 2014-03-19
WO2013004215A1 (fr) 2013-01-10
US20140290618A1 (en) 2014-10-02
BR112014000079A2 (pt) 2017-02-14
US9109530B2 (en) 2015-08-18

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