EP3746651A1 - Piston alternatif conçu pour un moteur à combustion interne à pistons alternatifs, et utilisation d'un piston alternatif dans un moteur à combustion interne à pistons alternatifs - Google Patents

Piston alternatif conçu pour un moteur à combustion interne à pistons alternatifs, et utilisation d'un piston alternatif dans un moteur à combustion interne à pistons alternatifs

Info

Publication number
EP3746651A1
EP3746651A1 EP19701634.8A EP19701634A EP3746651A1 EP 3746651 A1 EP3746651 A1 EP 3746651A1 EP 19701634 A EP19701634 A EP 19701634A EP 3746651 A1 EP3746651 A1 EP 3746651A1
Authority
EP
European Patent Office
Prior art keywords
piston
cooling
reciprocating piston
reciprocating
cooling channels
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
EP19701634.8A
Other languages
German (de)
English (en)
Other versions
EP3746651B1 (fr
Inventor
Paulo Ivan URZUA TORRES
Martin Bier
Alexander Lehnen
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.)
Volkswagen AG
Original Assignee
Volkswagen AG
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 Volkswagen AG filed Critical Volkswagen AG
Publication of EP3746651A1 publication Critical patent/EP3746651A1/fr
Application granted granted Critical
Publication of EP3746651B1 publication Critical patent/EP3746651B1/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
    • 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 invention relates to a reciprocating piston for a reciprocating internal combustion engine according to the preamble of claim 1.
  • the invention also relates to the use of such a reciprocating piston in a reciprocating internal combustion engine.
  • a liquid-cooled piston for an internal combustion engine wherein the piston in the region below a piston crown arranged in a star shape, has substantially radially extending cooling channels.
  • the cooling channels are connected to a ring channel disposed radially on the outer circumference of the piston, radially behind a piston skirt, with coolant entering the cooling channels by means of a coolant injection nozzle via a coolant supply and the annular channel.
  • a piston-axial coolant discharge is provided, wherein the coolant discharge discharges directly into the crank chamber arranged below the piston crown.
  • a piston which has an annular cooling channel. Coolant is fed into the piston via a connecting rod and a bolt connecting the connecting rod and the piston in the area of the piston pin hub.
  • the annular cooling passage is connected to the piston pin hub via a connecting passage extending in the axial direction. Furthermore, an outflow channel is provided, via which the coolant can flow out into the region immediately below a piston crown.
  • the invention has for its object to provide a reciprocating piston for a reciprocating internal combustion engine available, the improved cooling of the reciprocating piston as well as a further use of the cooling in one
  • An inventive reciprocating piston for a reciprocating internal combustion engine has a
  • Reciprocating internal combustion engine is oriented to a combustion chamber and the combustion chamber in the axial direction in one direction (usually down) dynamically limited.
  • the combustion chamber surface is sometimes referred to as upper piston crown.
  • the combustion chamber surface has a piston recess in the form of a depression in a middle region, viewed in the radial direction of the piston.
  • At least one cooling duct network i. such a cooling duct network is arranged either as a separately formed element and / or formed in one piece. If both variants are realized, i. the "and" combination of the above sentence is realized, the cooling duct network is partially formed separately and arranged in the reciprocating piston and partially in one piece in the
  • the cooling duct network has at least one inflow region, which is arranged on the inside in the radial direction of the main body, and a multiplicity of mini-cooling passages extending outwardly in the radial direction, starting from the inflow region.
  • the mini-cooling channels have a maximum cross-sectional width of 3 mm.
  • Combustor chamber surface or the body decreases - in particular in uncooled piston - viewed in the radial direction from radially inward to outside.
  • the reciprocating piston according to the invention it is provided by an inflow region arranged on the inside
  • the cooling liquid is also finely ramified and passed the surface to be cooled with many individual channels penetrating radially outwards, to cool even more radially outward portions of the body ,
  • the cooling liquid thus flows from a radial inner region in the direction of a radially outer region.
  • the cooling liquid can be used optimally for cooling, because the flow direction of the cooling liquid is thus at the temperature gradient of the body during operation of a
  • mini-cooling channels with a maximum cross-sectional width of 3 mm, makes it possible to provide a particularly large, available for cooling surface, so that there is a particularly efficient cooling of the body.
  • a cross-sectional size of the mini-cooling channels while the largest width is perpendicular to
  • the mini-cooling channels have in particular a maximum cross-sectional width of 2.5 mm and preferably the cross-sectional width of the cooling channels is at least 1 mm.
  • the cooling channels are formed in cross-section in particular circular. Alternatively, the cooling channels may also be polygonal in cross-section or have a different cross-sectional shape.
  • mini-cooling channels and cooling channels extending from the inside to the outside, the formation of so-called "hot spots", i. particularly hot areas, are targeted and efficiently counteracted on the base body of the reciprocating piston, in particular by arranging the mini-cooling channels so that at full load or other defined load condition results in a uniform temperature Temperarturver whatsoever on the combustion chamber surface. This also reduces the risk of pre-ignition - especially in gasoline engines.
  • the cooling of a reciprocating piston according to the invention can be further improved if the cooling channels lead to a radially outwardly arranged outflow opening or to a plurality of radially outwardly arranged outflow openings.
  • this one outflow opening or the plurality of outflow openings are in particular at least partially aligned such that coolant exiting through the outflow opening passes directly or indirectly on an outer side of a piston skirt.
  • a piston skirt is understood to mean, in particular, a section of the base body which is spaced apart-in particular below-a piston crown and the combustion chamber surface and generally has one or more guide surfaces for guiding the piston along a cylinder wall.
  • the coolant thus reaches - if at all - only indirectly (ie not directly) into the crankcase below the piston skirt.
  • cooling fluid is the Piston shirt cooled on the outside.
  • the coolant also improves the lubrication of the piston skirt and reduces its friction with the cylinder wall.
  • the outflow openings are in particular aligned such that the cooling liquid flows directly and thus directly from above onto the radial outer side of the piston skirt.
  • the outflow openings can also be aligned such that the cooling liquid initially collides against the cylinder wall and rebounds from there in the direction of the piston skirt.
  • the cooling channels or the at least one cooling channel in the region immediately adjacent to the outflow opening extend predominantly horizontally, i. essentially at an angle to the horizontal of at most 30 ° and preferably of not more than 20 ° and more preferably of not more than 10 °.
  • the horizontal plane is the direction perpendicular to the cylinder axis, along which the piston moves in the reciprocating internal combustion engine.
  • a gap between a radially outer portion of the piston skirt and a radially outer portion of a piston crown is formed on the body at least over part of the circumference, and at least one cooling channel leads into the region of the gap between the piston skirt and the piston bottom.
  • at least one cooling channel leads into the region of the gap between the piston skirt and the piston bottom.
  • a particularly efficient cooling of the piston according to the invention is achieved if in the base body at least eight (and preferably at least nine, at least ten or more) extending in the radial direction cooling channels are formed, because then there is already a relatively close-meshed distribution network with good surface penetration.
  • the cooling channels extend from the inflow region to eight, nine, ten or more corresponding outflow openings. It is also possible, the cooling channels so
  • Branching for example, by first of a radially inwardly arranged area 10 extend radially outward into a radially central region and these cooling channels then branch out starting from this central region in each case two or more further channels.
  • the cross-sectional width can be adjusted so that the
  • the maximum cross-sectional width is between 1 mm and 4 mm, preferably between 1 mm and 3 mm.
  • the projected area of the cooling channels is at least 20 percent, preferably at least 25 percent and more preferably at least 30 percent.
  • the inflow region comprises an annular channel or a central reservoir, and the cooling channels extend outwardly from this annular channel or the central reservoir in the radial direction.
  • ring is meant in this context preferably a closed, but also only part-ring-shaped designs, i. also semi-annular or other arcuate annular channel designs.
  • a good and homogeneous distribution of the cooling liquid can be achieved in the individual cooling channels, which allows a - considered in the circumferential direction - uniform piston crown cooling.
  • a central reservoir for example, hollow-spherical or otherwise shaped hollow-shaped, chamber-like structures are meant, from the outer sides of which the mini-cooling channels extend in the radial direction outwards.
  • a structurally particularly simple design results if at least two, flow-conducting not - or at least only up to a radially inwardly disposed network distribution point - interconnected cooling channel networks are formed in the body.
  • two or more cooling duct nets may be arranged so that the
  • Piston bottom is largely uniformly penetrated by channels of the cooling duct networks.
  • a first cooling duct network and a second cooling duct network may extend over two halves of the cross-sectional area of the main body.
  • the cooling channel networks are mirror images of each other. The two flow-conducting not interconnected
  • Cooling channel networks furthermore preferably have two flow areas which are separated from one another and can be fed independently of one another.
  • the formation of such separated inflow regions and cooling channel networks is particularly advantageous if the formation of the inflow region in the main body in a central position, i. radially center of the combustion chamber surface (in the region of the cylinder center axis) space engineering and / or constructive not or only with great effort to realize. This is the case in particular if the injection takes place via a piston injection nozzle (this will be explained in more detail below), since this can not be arranged centrally below the piston crown due to the connecting rod.
  • the at least one inflow region can extend starting from an inflow opening, which in the lateral surface of a
  • Piston pin hub is formed.
  • Such an embodiment of a reciprocating piston according to the invention is particularly suitable for the supply of the cooling duct network
  • Coolant via a connecting rod functionally connected to the reciprocating piston is then provided to form two flow channel non-interconnected cooling duct networks, wherein the inflow openings are formed on different sides of the connecting rod in the lateral surface of the piston pin hub.
  • the connecting rod is hollow inside, cooling fluid can be guided within the connecting rod in the direction of the reciprocating piston.
  • the reciprocating piston and the connecting rod are preferably connected by means of a bolt, wherein the bolt is in particular designed such that cooling fluid can be conveyed through the bolt to the at least one inflow opening.
  • at least one - in particular funnel-like - channel in the bolt be designed so that regardless of a pivotal movement between the connecting rod, pin and piston permanently sufficient coolant can be conveyed in the direction of the piston.
  • the at least one inflow opening extends in particular via a
  • Angular range of the circumference of the lateral surface of the piston pin hub corresponds at least to the angular range over which the bolt is pivoted during movement of the connecting rod relative to the reciprocating piston.
  • the bolt is connected in particular by means of press fit with the connecting rod and rotates relative to the reciprocating piston.
  • the inflow opening extends over at least 20 ° and preferably over at least 30 ° of the circumference of the lateral surface of the piston pin hub.
  • a pump may optionally be provided in a variant of the reciprocating piston according to the invention, with which a sufficiently high pressure is generated to during operation of the
  • Hubkolbenbrennkraftmaschine to fill at least 20 percent of the cooling duct network with coolant.
  • a pump can also be used for other purposes used standard oil pump a reciprocating internal combustion engine, but it can also be provided an additional pump for one or more reciprocating piston according to the invention, which is used exclusively or primarily for the supply of the cooling duct network. It is also possible to ensure the supply of the cooling duct network in any other way.
  • At least 25 percent, at least 30 percent or at least 40 percent, 50 percent or even 75 percent of the cooling duct network is filled with coolant.
  • Cooling duct network can also be completely (i.e., 100 percent) filled with cooling fluid, so that a particularly efficient cooling results due to a maximum flow through the cooling duct network with cooling fluid.
  • the cooling capacity can then be adjusted as needed, provided that the pump is controllable and / or regulated. If cooling liquid is introduced into the main body via a connecting rod, cooling liquid can be conveyed continuously, with high pressure and optionally also flow-controlled or flow-controlled active into the main body of the reciprocating piston.
  • the inflow region may in another embodiment of a region of the lower
  • Piston bottom extending, which is spaced from the piston pin hub.
  • Such an area is provided in particular adjacent to the piston pin hub and in particular as possible - as viewed in the radial direction - arranged centrally in the body, for example within a radius corresponding to a maximum of half the radius of the piston.
  • the supply of the cooling duct network with coolant takes place in particular via at least one piston injection nozzle.
  • the piston injection nozzle is preferably arranged below the lower piston crown in such a way that cooling liquid can be injected upwards into the cooling duct network.
  • two or more cooling channel networks, which are not connected to one another in terms of flow, are formed in the base body. More preferably, at least one separate piston spray nozzle is provided per cooling channel network.
  • the contour of the cooling channels is at least partially adapted to the contour of the combustion chamber surface such that the axial distance of the cooling channels to the combustion chamber surface is within a predetermined tolerance window.
  • the contour of the cooling channels is adapted to a combustion chamber surface with a piston recess, so that the cooling channels also have a trough-like contour.
  • both the axial distance of the cooling channels to the combustion chamber surface and to the lower piston crown lies within a predetermined tolerance window.
  • “Within the specified tolerance window” means here in particular that the distance deviation between the combustion chamber surface and / or the lower piston crown does not exceed 20 percent, preferably not more than 15 percent and more preferably not more than 10 percent.
  • the cooling channels preferably extend over at least 50 percent, preferably at least 65 percent and in particular at least 80 percent of the diameter of the piston head substantially horizontally. This means in particular the radially inward regions of the piston crown. More preferably, the cooling channels are at least partially adapted to the contour of the combustion chamber surface, i. the distance between the combustion chamber surface and the respective cooling channels is approximately constant at least over a partial region, preferably over the entire radial extension region of the cooling channels.
  • the inflow region is formed by an inflow opening, which is connected to the annular channel via a connecting channel extending in the axial direction.
  • the mini-cooling channels extend in the radial direction to the outside, wherein the contour of the cooling channels to the contour of the combustion chamber surface with a
  • Flask trough is adjusted.
  • the cooling channels initially extend in an axial section substantially in the axial direction and then open horizontally in a horizontal section into a region between the piston head and the piston skirt.
  • the invention also relates to the use of a reciprocating piston as described above in a reciprocating internal combustion engine.
  • the cooling liquid is introduced into the lifting piston via an inflow region arranged radially on the inside and is discharged outward in the radial direction through a multiplicity of cooling channels extending in the radial direction. It is caused by this use a particularly efficient cooling of the reciprocating piston, since the cooling liquid initially cools the particularly hot, radially central region of the combustion chamber surface and flows from there to the outside to the colder edge regions.
  • the cooling liquid is preferably introduced such that the at least one cooling channel network is filled to at least 20 percent with cooling liquid.
  • the cooling duct network is at least 30 percent or at least 40 percent, 50 percent or even at least 75 percent, and more preferably 100 percent filled with coolant. That is, the cooling liquid is introduced into the body at a sufficiently high pressure and / or speed to completely convey the cooling fluid through the mini-cooling channels. Overall, such an efficient cooling is achieved independently of a shaker effect.
  • Fig. 1 shows a first embodiment of a reciprocating piston according to the invention in one
  • FIG. 2 shows the reciprocating piston of FIG. 1 in a plan view
  • FIG. 3 is a half of the reciprocating piston of Fig. 1 and 2 in a perspective view obliquely from above,
  • FIG. 4 shows the reciprocating piston of FIGS. 1 to 3, wherein a piston skirt is shown in a longitudinal section according to line IV-IV of FIG. 2, and the region marked B in FIG. 4 is partially cut away, FIG.
  • Fig. 5 shows the reciprocating piston of FIGS. 1 to 4 in a longitudinal section along line V-V
  • FIG. 6 shows a cooling duct network shown in isolation in a perspective view
  • Fig. 7 shows the reciprocating piston of FIGS. 1 to 5 with a connecting rod and a bolt in one
  • Longitudinal section analogous to line VII-VII of FIG. 2, 8 shows a further embodiment with the cooling duct network from FIG. 6 and with a piston injection nozzle in a schematic illustration,
  • FIG. 9 shows a further embodiment of a reciprocating piston according to the invention in one
  • Fig. 10 the reciprocating piston of Fig. 9 without the piston crown in a perspective view obliquely from above.
  • the reciprocating piston 10 serves the known arrangement in a reciprocating internal combustion engine, not shown.
  • the reciprocating piston 10 viewed in the axial direction, moves up and down in the combustion chamber along the double arrow shown in FIG. 1, to the volume of one with the reciprocating piston
  • combustion chamber directed surface is referred to below combustion chamber surface 16 and may also be referred to as the upper piston crown.
  • the combustion chamber surface 16 comprises a radially centrally arranged piston recess 18.
  • the combustion chamber facing away from the side of the piston head 14 is referred to below as the lower piston head 20.
  • the main body 12 comprises a piston skirt 22 which, viewed in the axial direction, is arranged below the piston crown 14.
  • the piston skirt 22 is connected to the piston crown 14 via a piston pin hub 24.
  • the piston pin hub 24 serves for the pivotable connection of the lifting piston 10 with a connecting rod 26 by means of a bolt 28 (see Fig. 7).
  • a gap 30 extending in the axial direction is formed between the lower piston head 20 and the piston skirt 22 (cf., FIGS. 1 and 4), so that the piston skirt 22 is largely thermally decoupled from the piston crown 14.
  • the gap 30 extends over the entire area between the upper piston head 20 and the piston skirt 22.
  • two cooling channel networks 32 are formed, with the cooling channel networks 32 each extending over one half of the piston crown 14.
  • a cooling duct network 32 in each case comprises an inflow region 34 arranged on the inside as viewed in the radial direction.
  • the inflow region 34 is present, as can be seen in FIGS. 4 and 6, through an inflow opening 36 and upwardly from the inflow opening 36 in the axial direction extending connecting channel 38 and a in the
  • Substantially horizontally extending annular channel 40 is formed. Starting from the annular channel 40 extends in the radial direction outwardly a plurality of mini-cooling channels 42nd
  • mini-cooling channels 42 per cooling channel network 32, ten, in the radial direction extending mini-cooling channels 42 are formed (see Fig. 2 and Fig. 3).
  • the cross-sectional width of the mini-cooling channels 42 in the embodiment shown is 2.5 mm.
  • the cooling channels 42 extend to radially outwardly disposed outflow openings 44.
  • the outflow openings 44 are presently arranged in the region of the gap 30 between the piston skirt 22 and the lower piston crown 20, viewed in the axial direction.
  • the cooling channels 42 open into the region of the gap 30 between the lower piston crown 20 and the piston skirt 22. The coolant flowing through the cooling channels 42 is thereby guided such that it passes through the outflow openings 44 directly on the outside of the piston skirt 22.
  • cooling channels 42 The respective geometric design and respective directions of the individual cooling channels 42 can be clearly seen in particular in FIGS. 5 and 6.
  • the cooling channels 42 Starting from the annular channel 40, the cooling channels 42 initially extend largely horizontally outward.
  • the contour of the cooling channels 42 is adapted to the contour of the combustion chamber surface 16 with the piston recess 18. In particular, the distance between the cooling channels 42 and the
  • the cooling channels 42 extend over approximately 80 percent of the radially extending width (ie, diameter) of the combustion chamber surface 16 as viewed in the radial direction. Considering only the region in which the cooling channels 42 are approximately parallel to the Extend combustion chamber surface 16 in predominantly radial direction, the cooling channels 42 extend in the radial direction over about 60 percent of the width of the combustion chamber surface 16th
  • the cooling channels 42 are oriented in an axial section 46 mainly in the axial direction, before they pass into a further horizontal section 48 above the piston skirt 22 and there on each side to an outflow opening 44 to lead.
  • the inlet openings 36 are each funnel-shaped and extend over an angular range of the circumference of the lateral surface 54 of the piston pin hub 24, which permanently allows an inflow even when the connecting rod 26 pivots relative to the reciprocating piston 12 is.
  • the inflow openings 36 of the two cooling channel networks 32 are formed in the lateral surface 54 on respectively different sides of a connecting rod 26 connected to the reciprocating piston 10 (compare, see FIG. 2 and FIG.
  • FIG. 7 an arrangement of a reciprocating piston 10 according to the invention with a connecting rod 26 and a connecting rod 26 and the reciprocating piston 10 connecting pin 28 is shown.
  • the bolt 28 is here designed as a hollow cylindrical component with a support pin, which can be regarded as a partial element of the bolt and therefore has not received a separate reference numeral.
  • the connecting rod 26 is hollow in the present case, so that coolant through the interior of the
  • Pleuels 26 can be directed or actively pumped.
  • the bolt 28 has two at least partially extending in the axial direction channels 50, which lead to the inlet openings 36 of the respective cooling channel networks 32.
  • the bolt 28 rotates relative to the piston pin hub 24 by about 30 °.
  • the inflow openings 36 likewise extend over this angular range, so that an inflow of cooling liquid from the connecting rod 26 via the pin 28 into the respective cooling channel network 32 is made possible over the entire range of movement.
  • Fig. 8 shows another embodiment of a reciprocating piston according to the invention.
  • cooling liquid can also be introduced into the base body 12 by means of a piston injection nozzle 52.
  • the piston nozzle 52 is spaced from the respective inflow opening 36 so arranged that cooling liquid as a jet in the direction of
  • the cooling channel nets 32 may be opposite those shown in FIG.
  • Cooling channel networks 32 may be arranged rotated by 90 ° about the cylinder axis, so that an injection from below the lower piston crown 20 in the radial direction, as viewed farther outward and spaced from the piston pin hub 24 takes place. It is hereby accepted that the injection takes place at a distance from the center of the combustion chamber surface 16.
  • the geometry of the cooling duct network 32 can be adapted such that coolant is first conveyed from a radially outer inlet opening 36 into a central region of the combustion chamber surface 16 and from there - possibly after further promotion in the direction of the combustion chamber surface 16 - via the cooling channels 42 flows in the radial direction to the outside.
  • FIGS. 9 to 10 show a further embodiment of a reciprocating piston 10.
  • This embodiment of the reciprocating piston 10 differs from the first embodiment in particular in that the piston skirt 22 is externally connected to the lower piston crown 20. Consequently, no gap 30 is formed between the lower piston crown 20 and the piston skirt 22.
  • the outflow openings 44 are formed such that they pass through the piston skirt 22, so that cooling liquid to the outside of the
  • Piston shirt 22 can get.
  • the features of the invention disclosed in the present description, in the drawings and in the claims can be used individually as well as in any desired manner

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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)

Abstract

L'invention concerne un piston alternatif conçu pour un moteur à combustion interne à pistons alternatifs comprenant un corps de base (12) et une surface de chambre de combustion (16). Au moins un réseau de canaux de refroidissement (32) est prévu dans le corps de base (12). Ce réseau de canaux de refroidissement (32) comprend au moins une zone d'afflux (34) agencée côté intérieur lorsqu'elle est observée dans la direction radiale du corps de base (12), ainsi qu'une pluralité de mini-canaux de refroidissement (42) s'étendant respectivement vers l'extérieur dans la direction radiale à partir de la zone d'afflux (34), les mini-canaux de refroidissement (42) présentant une largeur de section transversale maximale de 3 mm. Cette invention se rapporte en outre à l'utilisation d'un piston alternatif (10) dans un moteur à combustion interne à pistons alternatifs.
EP19701634.8A 2018-02-01 2019-01-23 Piston alternatif conçu pour un moteur à combustion interne à pistons alternatifs, et utilisation d'un piston alternatif dans un moteur à combustion interne à pistons alternatifs Active EP3746651B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102018201556.2A DE102018201556A1 (de) 2018-02-01 2018-02-01 Hubkolben für eine Hubkolbenbrennkraftmaschine und Verwendung eines Hubkolbens in einer Hubkolbenbrennkraftmaschine
PCT/EP2019/051649 WO2019149598A1 (fr) 2018-02-01 2019-01-23 Piston alternatif conçu pour un moteur à combustion interne à pistons alternatifs, et utilisation d'un piston alternatif dans un moteur à combustion interne à pistons alternatifs

Publications (2)

Publication Number Publication Date
EP3746651A1 true EP3746651A1 (fr) 2020-12-09
EP3746651B1 EP3746651B1 (fr) 2023-05-24

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EP19701634.8A Active EP3746651B1 (fr) 2018-02-01 2019-01-23 Piston alternatif conçu pour un moteur à combustion interne à pistons alternatifs, et utilisation d'un piston alternatif dans un moteur à combustion interne à pistons alternatifs

Country Status (4)

Country Link
EP (1) EP3746651B1 (fr)
CN (1) CN111868367B (fr)
DE (1) DE102018201556A1 (fr)
WO (1) WO2019149598A1 (fr)

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WO2023274739A1 (fr) 2021-07-01 2023-01-05 IFP Energies Nouvelles Piston pour moteur a combustion interne avec systeme de refroidissement optimise

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DE102011119525A1 (de) * 2011-11-26 2013-05-29 Mahle International Gmbh Kolben für einen Verbrennungsmotor
CN102705101A (zh) * 2012-05-16 2012-10-03 郑凌 内燃机活塞的冷却系统
DE102013009164A1 (de) * 2013-05-31 2014-12-04 Mahle International Gmbh Kolben für einen Verbrennungsmotor
US9228480B2 (en) * 2014-06-06 2016-01-05 Mahle Industries, Incorporated Piston crown cooling gallery insert
US10184422B2 (en) * 2014-12-30 2019-01-22 Tenneco Inc. Reduced compression height dual gallery piston, piston assembly therewith and methods of construction thereof
JP2016151409A (ja) * 2015-02-19 2016-08-22 本田技研工業株式会社 ヒートパイプ、並びにヒートパイプを備えたピストン及び吸排気バルブ
DE102015005542A1 (de) * 2015-04-29 2016-11-03 Daimler Ag Kolben für eine Hubkolben-Verbrennungskraftmaschine
US10352270B2 (en) * 2016-03-01 2019-07-16 Tenneco Inc. Galleryless piston with connection to pockets
JP2017190713A (ja) 2016-04-13 2017-10-19 トヨタ自動車株式会社 内燃機関

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2023274739A1 (fr) 2021-07-01 2023-01-05 IFP Energies Nouvelles Piston pour moteur a combustion interne avec systeme de refroidissement optimise
FR3124829A1 (fr) 2021-07-01 2023-01-06 IFP Energies Nouvelles Piston pour moteur à combustion interne avec système de refroidissement optimisé

Also Published As

Publication number Publication date
CN111868367B (zh) 2022-05-27
EP3746651B1 (fr) 2023-05-24
WO2019149598A1 (fr) 2019-08-08
DE102018201556A1 (de) 2019-08-01
CN111868367A (zh) 2020-10-30

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