EP1198667B1 - Piston refroidi par liquide - Google Patents

Piston refroidi par liquide Download PDF

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Publication number
EP1198667B1
EP1198667B1 EP00949192A EP00949192A EP1198667B1 EP 1198667 B1 EP1198667 B1 EP 1198667B1 EP 00949192 A EP00949192 A EP 00949192A EP 00949192 A EP00949192 A EP 00949192A EP 1198667 B1 EP1198667 B1 EP 1198667B1
Authority
EP
European Patent Office
Prior art keywords
piston
cooling channel
cooling
wave
channel
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.)
Expired - Lifetime
Application number
EP00949192A
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German (de)
English (en)
Other versions
EP1198667A1 (fr
Inventor
Edgar Martin
Stephan Thieme
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.)
Federal Mogul Nuernberg GmbH
Original Assignee
Federal Mogul Nuernberg GmbH
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Filing date
Publication date
Application filed by Federal Mogul Nuernberg GmbH filed Critical Federal Mogul Nuernberg GmbH
Publication of EP1198667A1 publication Critical patent/EP1198667A1/fr
Application granted granted Critical
Publication of EP1198667B1 publication Critical patent/EP1198667B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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 invention relates to a liquid-cooled piston according to the preamble of claim 1.
  • the pistons of internal combustion engines are subjected to high thermal loads due to the combustion occurring in the combustion chamber.
  • a piston according to the preamble of claim 1 is known from DE-OS 30 19 953.
  • This piston has an annular channel adjacent to a hole open towards the crankcase, through which the cooling oil can flow.
  • the oil flows in these known pistons through an outlet bore, which is provided approximately in the center of the piston (seen in plan view).
  • the annular channel is completely at a certain height of the piston. This will be a useful cooling of the land section, so the area located behind the piston rings, as well as the area reached below the combustion bowl.
  • the particularly highly loaded in high-speed diesel engines pin bosses and the surrounding area are insufficiently cooled.
  • the star-shaped cooling channels are designed so that they cool in particular the area behind the rings and the area of the combustion bowl. A satisfactory cooling of the pin boss area can only be ensured by the provision of complicated casting cores, which can be removed from the finished piston only with great effort.
  • cooling channels of the piston according to DE 196 18 625 C1 are comparatively simple in design, they are so far away from the region of the pin boss that sufficient cooling does not take place in this zone.
  • DE 197 36 135 C1 discloses a liquid-cooled piston with a cooling channel, which extends with two separate legs, starting from a radial edge region to the middle obliquely upward and then obliquely downward to the opposite radial edge region. Seen in plan view, the two legs form an overall X-shaped configuration. As a result, an improved cooling of the piston crown is to be achieved.
  • the invention has for its object to provide an easy-to-manufacture liquid-cooled piston, which has a good cooling of both the annular region and the pin boss area, wherein the demands placed on the piston strength requirements should continue to be met.
  • the cooling channel of the piston according to the invention which is seen in total as a whole in plan view is substantially annular or consists of a plurality of ring segments, formed wave-shaped in the direction of the piston axis.
  • the cross section of the cooling channel remains substantially the same over the entire course of the cooling channel, so that, for example, in contrast to the piston according to DE-PS 17 51 342 no unnecessary complication of the shape of the cooling channel is required.
  • the cooling channel extends with a substantially constant cross-section seen in a side view of the piston wave-shaped, so that it reaches from the area behind the piston rings in each case partially closer to the pin boss area, as is the case with the known pistons.
  • a reliable cooling of both of these areas can be achieved.
  • Due to the undulating shape there is also the advantage that the cooling channel becomes longer overall, so that it has a cooling surface which is larger than that of conventional cooling channels, and the cooling capacity is increased.
  • the wave-shaped course of the cooling channel allows a smaller distance between the cooling channel and the ring carrier, since in the troughs each sufficient material remains behind the ring carrier, and thus a total of the strength requirements is satisfied.
  • the wave-shaped course of the cooling channel also causes the cooling oil, unlike in known at a level remaining cooling channels, not directly flows through it, but with a longer residence time remains in the cooling channel, and thus can absorb more heat.
  • the cooling of the areas surrounding the cooling channel is not only from a single side. In a sense, the cooling channel cools the adjacent areas not only from the cooling channel, but when considering a wave trough cooling takes place both from the wave trough, as well as from the two adjacent wave crests in the direction of Corrugation. Also by this mode of operation, the cooling performance can be improved.
  • a shape of the cooling channel has proved to be particularly advantageous, in which the distance between wave trough and wave crest is more than 1.5 times the cooling channel cross-section.
  • the distance measured in the direction of the piston axis from the lowest point of a wave trough to the highest point of a wave crest is at least 1.5 times the distance between the lowest point of a wave trough and the highest point of the cooling channel in the trough, which corresponds to the cooling channel cross section ,
  • the measures according to the invention make it possible for the wall thickness between the cooling channel and ring carriers to be reduced to 0-10 mm, preferably 0-5 mm, in particular 0-2 mm.
  • the wall thickness between the cooling channel and ring carriers can be reduced to 0-10 mm, preferably 0-5 mm, in particular 0-2 mm.
  • the shape of the wave-shaped cooling channel is preferred that it has an odd number of complete waves in one half of its annular course.
  • an odd number of To detect wave crests so that there is a wave crest in the area above the pin eye.
  • a trough would be located here, so that in certain situations insufficient material strength remains between the trough and the pin eye.
  • undesirable weakening of the piston can be reliably avoided if the number of waves is odd, so that above the pin bore a wave crest is that adapts particularly favorable in terms of its shape to the course of the upper half of the pin eye.
  • an oval shape has proven to be particularly advantageous, wherein it is preferred for it to be oriented outwardly inclined.
  • the upper portion of the oval-shaped cooling passage is closer to the outer wall of the piston than the lower portion.
  • the piston 10 of the invention is shown in a side view in the direction of the pin boss 12.
  • the piston 10 shown schematically has a ring carrier 14.
  • the region of the ring carrier 14, as well as the region in the vicinity of the pin boss 12, is to be cooled particularly reliably.
  • a (seen in plan view) largely annular, parallel to the circumference of the piston extending cooling channel 16 is provided.
  • the cooling channel 16 extends in the form of a wave in the direction of the piston axis 18 such that it extends between these regions.
  • a wave crest 20 is provided in a particularly advantageous manner above the pin boss 12, which ensures reliable cooling of the area with the ring carrier 14 together with the other crests.
  • a comparatively small wall thickness remains between the wave crests 20 and the ring carrier 14, the overall strength is ensured since in the region of the wave troughs 22 the wall thickness behind the ring carrier 14 is not reduced so much.
  • the cooling channel 16 extends in these sections particularly close to the pin boss 12, so that their surroundings can also be cooled well. 1, the preferred embodiment according to which the number of complete wave crests in one half of the cooling channel is odd, is located in the example shown in FIG. 1 above the pin boss 12, a wave crest, so that also in this area sufficient wall thickness remains.
  • This area is different in the embodiment shown in more detail in FIG. 2.
  • a suitable design of the wave-shaped cooling channel 16 By means of a suitable design of the wave-shaped cooling channel 16, however, a sufficient material thickness can also be achieved in this embodiment in the area above the bolt eye 12.
  • a ring carrier 14 can be seen in detail, to which the cooling channel 16 in the region of the wave crests reaches comparatively close. 2
  • the cooling channel 16 is designed in the example shown with an oval extending in the direction of the piston axis 18, wherein this is inclined slightly outwards.
  • the distance from the lowest point of a wave trough 22 to the highest point of a wave crest 20 is approximately twice the cooling channel cross section, as can be seen in the side view of FIG. 2.
  • FIG. 3 the interior of the cooling channel 16 is shown in a perspective view.
  • a casting core which is introduced during the casting of the piston 10 according to the invention would have approximately the shape shown in FIG. 3.
  • the illustration shows that the cooling channel 16 in the example shown has two diametrically opposite inflow points.
  • the cooling channel 16 is formed overall by two ring-segment-shaped sections as seen in plan view, each of which almost corresponds to the drainage region Have the shape of a semicircle. In this way, together with the inlet or outlet regions 26, a generally largely annular shape of the cooling channel 16 results.
  • the cooling channel first extends as far as a first wave crest 20a in the direction of the piston crown.
  • the other half of the overall annular cooling channel 16 is designed in a similar manner.
  • the odd number of five complete waves in the half of the cooling channel 16 explained above causes a wave crest, designated 20c in the shown case, to be located above the pin eye.
  • the required wall thickness can be ensured in all areas, with reliable cooling of the area in the vicinity of the pin eye being achieved, in particular, by the adjacent wave troughs 22b and 22c.
  • the cooling channel extends with the interior shown in Fig. 3 particularly close to the ring carrier of the piston, so that this area is reliably cooled. Furthermore, there is a larger inner surface of the Cooling channel, compared with a course of the cooling channel, which remains at a certain level, as well as a longer residence time of the cooling oil, so that the cooling capacity can be increased overall. As can be seen from Fig. 3, results for the shape of the interior of the cooling channel 16 a total of a "crown-like" shape.

Landscapes

  • 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)
  • Separation By Low-Temperature Treatments (AREA)

Claims (4)

  1. Piston (10) refroidi par liquide, pour des moteurs à combustion, comprenant un canal de refroidissement (16) à forme annulaire ou formé de plusieurs segments d'anneau, présentant une section transversale largement constante dans son évolution, caractérisé en ce que le canal (16) s'étend, au moins par tronçons, selon une forme ondulée en direction de l'axe de piston (18), et en ce que l'espacement, entre une vallée d'ondulation et un sommet d'ondulation, est supérieur à 1,5 fois la dimension du canal de refroidissement en direction de l'axe de piston (18).
  2. Piston selon la revendication 1, caractérisé en ce que l'épaisseur de paroi, entre le canal de refroidissement (16) et les supports annulaires (14), est diminuée à 0 à 10 mm, de préférence à. 0 à 5 mm, en particulier à 0 à 2 mm.
  3. Piston selon la revendication 1 ou 2, caractérisé en ce que le nombre des ondulations complètes dans une moitié du canal de refroidissement (16) est impair, faisant qu'un sommet d'ondulation (20c) se trouve au-dessus de l'oeillet de boulon (12).
  4. Piston selon l'une de revendications précédentes, caractérisé en ce que la section transversale du canal de refroidissement (16) est sensiblement ovale et, de préférence, est orientée inclinée vers l'extérieur.
EP00949192A 1999-07-02 2000-06-19 Piston refroidi par liquide Expired - Lifetime EP1198667B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19930630 1999-07-02
DE19930630A DE19930630C1 (de) 1999-07-02 1999-07-02 Flüssigkeitsgekühlter Kolben
PCT/EP2000/005633 WO2001002713A1 (fr) 1999-07-02 2000-06-19 Piston refroidi par liquide

Publications (2)

Publication Number Publication Date
EP1198667A1 EP1198667A1 (fr) 2002-04-24
EP1198667B1 true EP1198667B1 (fr) 2006-02-08

Family

ID=7913478

Family Applications (1)

Application Number Title Priority Date Filing Date
EP00949192A Expired - Lifetime EP1198667B1 (fr) 1999-07-02 2000-06-19 Piston refroidi par liquide

Country Status (9)

Country Link
US (1) US6499386B2 (fr)
EP (1) EP1198667B1 (fr)
JP (1) JP2003526755A (fr)
AT (1) ATE317497T1 (fr)
BR (1) BR0011981B1 (fr)
DE (2) DE19930630C1 (fr)
ES (1) ES2256023T3 (fr)
PL (1) PL198900B1 (fr)
WO (1) WO2001002713A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102016004699A1 (de) 2016-04-16 2016-12-22 Daimler Ag Kolben für eine Hubkolbenmaschine

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Publication number Priority date Publication date Assignee Title
DE10106435A1 (de) * 2001-02-13 2002-08-14 Bayerische Motoren Werke Ag Kolben, insbesondere für eine Brennkraftmaschine
DE10126359B4 (de) * 2001-05-30 2004-07-22 Federal-Mogul Nürnberg GmbH Kolben für einen Verbrennungsmotor
DE10158607B4 (de) * 2001-11-29 2005-10-06 Federal-Mogul Nürnberg GmbH Flüssigkeitsgekühlter Kolben für Verbrennungskraftmaschine
DE10218999B4 (de) * 2002-04-27 2005-03-03 Ks Kolbenschmidt Gmbh Kolben mit Ringträger und Formkühlkanal
DE10244513A1 (de) * 2002-09-25 2004-04-08 Mahle Gmbh Mehrteiliger gekühlter Kolben für einen Verbrennungsmotor und Verfahren zu dessen Herstellung
DE102004043720A1 (de) * 2004-09-09 2006-03-30 Federal-Mogul Nürnberg GmbH Kolben für einen Verbrennungsmotor sowie Verbrennungsmotor
DE102004056870A1 (de) * 2004-11-25 2006-06-01 Mahle International Gmbh Kolben mit einem Kühlkanal für einen Verbrennungsmotor und Verfahren zur Herstellung des Kolbens
DE202006020280U1 (de) * 2006-11-28 2008-02-21 Ks Kolbenschmidt Gmbh Kühlkanalkolben
DE102006056012A1 (de) 2006-11-28 2008-05-29 Ks Kolbenschmidt Gmbh Variabel gestalteter Kühlkanal für einen Kolben
DE102006056011A1 (de) * 2006-11-28 2008-05-29 Ks Kolbenschmidt Gmbh Kühlkanalvarianten für Kolben
DE102008002571A1 (de) 2008-06-20 2009-12-31 Federal-Mogul Nürnberg GmbH Kolben für einen Verbrennungsmotor
DE102009001888C5 (de) * 2009-03-26 2019-12-24 Federal-Mogul Nürnberg GmbH Kolben für einen Verbrennungsmotor
US9970384B2 (en) 2009-11-06 2018-05-15 Federal-Mogul Llc Steel piston with cooling gallery and method of construction thereof
US8807109B2 (en) * 2009-11-06 2014-08-19 Federal-Mogul Corporation Steel piston with cooling gallery and method of construction thereof
DE102010020227B4 (de) 2010-05-11 2023-10-26 Ks Kolbenschmidt Gmbh Verfahren zur Erzeugung einer beliebig gestalteten Geometrie an Kolben von Brennkraftmaschinen und eine Vorrichtung zur Durchführung des Verfahrens
DE102010051033A1 (de) 2010-11-11 2012-05-16 Daimler Ag Flüssigkeitsgekühlter Kolben eines Verbrennungsmotors
US8863381B2 (en) * 2010-12-22 2014-10-21 GM Global Technology Operations LLC Method of making a piston oil gallery using a hollow metallic core
DE102011076455A1 (de) * 2011-05-25 2012-11-29 Mahle International Gmbh Gießkern zur Bildung eines Kühlkanals in einem Kolben
JP2014185522A (ja) * 2013-03-21 2014-10-02 Hitachi Automotive Systems Ltd 内燃機関のピストン
DE102015213689A1 (de) * 2015-07-21 2017-01-26 Federal-Mogul Nürnberg GmbH Kolben für einen Verbrennungsmotor
MX2018013353A (es) 2016-05-04 2019-02-20 Ks Kolbenschmidt Gmbh Piston.
CN108999717A (zh) * 2018-08-15 2018-12-14 全椒县全动机械有限公司 一种柴油机活塞结构
GB2578803B (en) * 2019-04-04 2020-12-16 Cox Powertrain Ltd Marine outboard motor with piston cooling gallery
CN110513182A (zh) * 2019-09-25 2019-11-29 深圳臻宇新能源动力科技有限公司 活塞冷却系统
DE102020000321A1 (de) 2020-01-21 2021-07-22 Ford Global Technologies, Llc Brennkraftmaschine mit gekühltem Kolben und Verfahren zur Herstellung eines zugehörigen Kolbens

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US4180027A (en) * 1977-07-20 1979-12-25 Mack Trucks, Inc. Two-piece oil-cooled piston
IT1118774B (it) 1979-06-12 1986-03-03 Ass Eng Italia Perfezionamento relativo aglistantuffi nei motori diesel
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DE19618625C1 (de) * 1996-05-09 1997-10-23 Daimler Benz Ag Flüssigkeitsgekühlter Kolben für Verbrennungsmotoren
DE19736135C1 (de) * 1997-08-20 1998-10-29 Daimler Benz Ag Flüssigkeitsgekühlter Kolben für Verbrennungsmotoren
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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102016004699A1 (de) 2016-04-16 2016-12-22 Daimler Ag Kolben für eine Hubkolbenmaschine

Also Published As

Publication number Publication date
BR0011981B1 (pt) 2010-07-27
EP1198667A1 (fr) 2002-04-24
DE50012199D1 (de) 2006-04-20
DE19930630C1 (de) 2000-10-26
WO2001002713A1 (fr) 2001-01-11
ATE317497T1 (de) 2006-02-15
PL198900B1 (pl) 2008-07-31
ES2256023T3 (es) 2006-07-16
BR0011981A (pt) 2002-03-19
PL353177A1 (en) 2003-11-03
US6499386B2 (en) 2002-12-31
JP2003526755A (ja) 2003-09-09
US20020162448A1 (en) 2002-11-07

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