EP0189767A2 - Piston à plusieurs parties, refroidi par de l'huile, pour moteurs à combustion interne à piston alternatif - Google Patents

Piston à plusieurs parties, refroidi par de l'huile, pour moteurs à combustion interne à piston alternatif Download PDF

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Publication number
EP0189767A2
EP0189767A2 EP86100309A EP86100309A EP0189767A2 EP 0189767 A2 EP0189767 A2 EP 0189767A2 EP 86100309 A EP86100309 A EP 86100309A EP 86100309 A EP86100309 A EP 86100309A EP 0189767 A2 EP0189767 A2 EP 0189767A2
Authority
EP
European Patent Office
Prior art keywords
piston
wall
oil
piston part
cooling
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
EP86100309A
Other languages
German (de)
English (en)
Other versions
EP0189767B1 (fr
EP0189767A3 (en
Inventor
Horst Lindner
Jordan Gentscheff
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.)
MAN B&W Diesel GmbH
Original Assignee
MAN B&W Diesel 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 MAN B&W Diesel GmbH filed Critical MAN B&W Diesel GmbH
Publication of EP0189767A2 publication Critical patent/EP0189767A2/fr
Publication of EP0189767A3 publication Critical patent/EP0189767A3/de
Application granted granted Critical
Publication of EP0189767B1 publication Critical patent/EP0189767B1/fr
Expired 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
    • F02F3/225—Pistons  having cooling means the means being a fluid flowing through or along piston the fluid being liquid the liquid being directed into blind holes
    • 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 
    • F02F3/0015—Multi-part pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M1/00—Pressure lubrication
    • F01M1/08—Lubricating systems characterised by the provision therein of lubricant jetting means
    • F01M2001/086—Lubricating systems characterised by the provision therein of lubricant jetting means for lubricating gudgeon pins
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
    • F05C2201/00—Metals
    • F05C2201/02—Light metals
    • F05C2201/021—Aluminium
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
    • F05C2201/00—Metals
    • F05C2201/04—Heavy metals
    • F05C2201/0433—Iron group; Ferrous alloys, e.g. steel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
    • F05C2201/00—Metals
    • F05C2201/04—Heavy metals
    • F05C2201/0433—Iron group; Ferrous alloys, e.g. steel
    • F05C2201/0448—Steel

Definitions

  • the invention relates to an oil-cooled, multi-part plunger for reciprocating internal combustion engines with features as specified in the preamble of claim 1.
  • Such an oil-cooled plunger is known from DE-OS 1 526 598.
  • the lower piston part is made of aluminum, while the upper piston part is made of a steel material.
  • Such a piston is particularly unsuitable for very high ignition pressures because of the aluminum lower piston part, because the deformation of the lower piston part becomes very large under the acting ignition pressures, which could cause piston seizures.
  • This disadvantage could be remedied by producing the lower piston part with a corresponding ovality and crowning so that it can absorb the deformation resulting from the action of the ignition pressures.
  • the piston to be created should be designed to provide more favorable cooling oil guidance for the best effect of the cooling oil to be passed through, in particular with a view to reducing the amount of oil to be carried out; furthermore, the piston to be created, while avoiding a large number of lubricating oil scraper rings for a given low lubricating oil consumption, should enable such favorable lubricating oil regulation that the oil present is in any case so distributable that at places on the circumference of the piston where lubricating oil is absolutely necessary, e.g. on the cylinder running surface in the area of the pressure and counter pressure side of the piston, is lubricated more intensively than at other circumferential locations of the piston.
  • the upper piston part is made of nodular cast iron or steel material
  • the lower part of the piston is made of gray cast iron or nodular cast iron
  • the material can also be used to take account of extremely high loads that will occur later in operation.
  • the ignition pressures acting on the plunger during operation are further enhanced by the dome-like design of the piston-bolt carrying chair according to the invention the special support of the upper piston part on the lower piston part as well as the dome-like limitation of the internal cooling space are taken into account.
  • the cooling oil guide according to the invention in the piston not only achieves a very favorable cooling effect; by appropriate distribution of the transfer bores between the inner and outer cooling space, in particular by different distances between them with a corresponding clustering and size and inclination dimensioning, the uneven temperature distribution acting in the upper piston part can be influenced so favorably that uneven deformations of the piston crown in the radial direction can be avoided.
  • the latter in conjunction with the support of the piston upper part according to the invention in the region of its bending-neutral zone, contributes to the fact that its outer wall remains largely cylindrical even under the action of the thermal and mechanical load.
  • the inventive design of the lower edge of the lower piston part also advantageously achieves that effect that there is always sufficient lubricating oil on the cylinder wall on the pressure side of the plunger and its counterpressure side, while in the remaining peripheral regions of the plunger, in which no such heavy lubrication is required is that the lubricating oil is largely stripped off the cylinder running surface when the plunger moves downward.
  • the oil-cooled plunger shown in the drawing consists of a piston lower part, generally designated 1, and an upper piston section, generally designated 2.
  • the one-piece upper piston part 2 comprises a piston crown 3 and an outer wall 4 with a cylindrical outer surface 5 and a plurality of ring grooves, into which piston rings 6 are inserted.
  • the outer wall 4 of the piston upper part 2 is composed of a wall section 7 of large cross-section adjoining the piston crown 3 and a wall section 9 of smaller diameter adjoining its lower edge 8.
  • an undercut 10 with a circular-cylindrical centering surface 11 and a contact surface 12 perpendicular to the piston axis is formed in the cross-sectional wall part 7 of the outer wall 4.
  • the upper piston part “2 is supported on the outer end face 13 of a support collar 14, which is formed on the upper side of a piston bolt support chair designated by 15 and forming part of the lower piston part 1.
  • the upper piston part 2 is in this exemplary embodiment via the circular-cylindrical centering surface 11 centered with respect to the lower piston part 1 on a circular cylindrical centering surface 16 formed thereon on the supporting collar 4.
  • an axially projecting supporting collar 17 is formed on the inside of the piston crown 3, which has a contact surface 18 at the bottom transverse to the longitudinal axis of the piston With this contact surface 18, this upper piston part 2 is supported on the end face 13 of the support collar 14.
  • this upper piston part 2 is supported via the lower edge 19 of its outer wall 4 on the upper edge 20 of the outer wall of the lower piston part 1, generally designated 21.
  • This upper piston is centered Part 2 here by a circular cylindrical outer surface 22, arranged coaxially to the longitudinal axis of the piston, of a centering collar 23 projecting above the upper edge 20, against which the outer wall 4 of this upper piston part 2 rests with its inner surface 24 which is circular cylindrical in the lower region.
  • the upper piston part 2 is fastened to the lower piston part 1 generally by means of a plurality of clamping screws 25, which are only indicated by dash-dotted lines in the drawing.
  • a piston pin is designated, which is anchored in a bearing bore 27 which penetrates the piston piston support frame 15 in the lower piston part 1.
  • a bearing sleeve 28 sits on this piston pin 26, the position of which is fixed between fixing surfaces 29, 30 and 31, 32 parallel to the longitudinal axis of the piston.
  • the plunger is articulated via the piston pin 26 and the bearing sleeve 28 seated thereon to a connecting rod 33 connected to the crankshaft (not shown) of a reciprocating piston internal combustion engine in the region of the connecting rod head 34, this connection being produced via a receiving bore 35 which penetrates the connecting rod head 34 transversely and encompasses the bearing sleeve 28 is.
  • a projection is designated, which is arranged on the upper side 37 of the piston bolt support chair 15 and either - as shown in Figures 1 to 3 - formed in one piece with the latter or - as shown in Figure 4 - only in one piece with the lower part Piston-bolt support chair 15 can be formed, in which case the upper section is realized by a tubular attachment piece 38.
  • This protrusion 36, 38 like the piston-piston carrying chair 15, is penetrated overall by a central cooling oil passage hole 39 arranged coaxially to the piston longitudinal axis.
  • the projection 36, 38 generally protrudes into the area of the piston upper part 2 and, with its upper edge 40, limits the cooling oil fill level of an inner cooling space, which is designated overall by 41.
  • the latter is delimited in its lower region by the inner surface 42 of the support collar 14, furthermore the upper side 37 of the piston bolt support chair 15 and the outer surface 43 of the projection 36, 38 and in its upper region by a recess in the upper piston part 2.
  • This inner cooling space 41 is connected via inclined transfer holes 44 formed in the upper piston part 2 to an outer cooling space, designated overall by 45, which extends both in the upper piston part 2 and in the lower piston part 1, there around the supporting collar 14.
  • the upper piston part 2 is made in one piece from nodular cast iron or steel material, while the lower piston part 1 is also made in one piece from gray cast iron or nodular cast iron.
  • the plunger is designed for a special type of shaker cooling; the cooling oil is supplied from the connecting rod 33 through a feed bore 46, an annular channel 47 around the bearing sleeve 28 and a spray bore 48 in the connecting rod head 34 through the cooling oil passage hole 39 into the inner cooling space 41. From there, the cooling oil, as a result of the piston movements during operation, passes through the transfer bores 44 into the outer cooling chamber 45 and from there via outlet openings 49 arranged in its lower region back into the engine room of the reciprocating piston internal combustion engine.
  • the inner cooling space 41 is provided by a dome-like cavity, which is radially on the outside by a correspondingly curved shape of the inner wall 42 of the support collar 14, and subsequently by a correspondingly continuously curved shape in the case of the plunger from FIGS. 1 to 3 of the inner surface 50 of the cross-sectionally large wall part 7 the outer wall 4 of the upper piston part 2 or, in the case of the plunger of FIG. 4, the inner surface 51 of the support collar 17 and then subsequently formed by a correspondingly continued curvature of the inner surface 52 of the piston crown 3.
  • an elevation 53 is provided on the inner surface 52 of the piston crown 3, which contributes to a favorable introduction and distribution of the cooling oil in the inner cooling space 41.
  • the outer cooling chamber 45 is in the plunger according to Fig.l to 3 in the area of the piston upper part 2 on the one hand by several on the circumference, slightly obliquely with respect to the piston longitudinal axis from the lower edge 8 of the cross-sectional wall part 7 of the outer wall 4 formed in the latter, and on the other hand through an annular space 55 is formed, into which the blind holes 54 open.
  • a transition bore 44 opens into each blind hole 54, which branches off from the inner cooling space 41 in the area of the inner surface 50 of the wall section 7 with a large cross section and diagonally upwards into the associated one Blind hole 54 opens near its closed end.
  • the space 55 is delimited radially on the outside by the inner surface 56 of the lower-section lower wall part 9 of the outer wall 4 of the upper piston part 2 and radially on the inside by the outer surface 57 of the support collar 14 and above by the lower edge 8 of the thick-section wall part 7 of the outer wall 4 of the upper piston part 2.
  • the outer cooling space 45 continues downward within the lower piston part 1 through an annular space 58 which extends down to the piston-piston carrying chair 15.
  • the outer cooling space 45 in the region of the piston upper part 2 is formed by an annular upper cooling chamber part 59, which is delimited on the outside by the inner surface 24 of the outer wall 4 of the upper piston part 2, on the inside by the outer surface 60 of the support collar 17 and downwards an existing in the lower piston part 1 of the lower cooling chamber part 61 is open, which, like in the exemplary embodiment according to FIGS.
  • the piston pin support chair 15 is generally dome-like, like the boundary wall of the inner cooling space 41, that is to say designed in the manner of a hollow spherical section-shaped dome, in such a way that it surrounds the connecting rod head 34, which has an essentially round outer contour 62 within the lower piston part 1, with a small clearance.
  • this dome-shaped piston pin supporting chair 15 has bearing eyes 63 and 64 on both sides of the connecting rod head 34, as can be seen in FIG. 2, which are penetrated by the bearing bore 27 and serve to receive the piston pin ends projecting on both sides of the connecting rod head 34.
  • the outer wall 21 of the piston lower part 1 is interrupted in each case by an opening 65 or 66 through which the piston pin 26 is assembled.
  • the dome-shaped piston pin support chair 15 preferably has a wall thickness which is essentially the same everywhere, so that the part of the outer cooling space 45 present in the lower piston part 1 partially extends down to the level of the piston pin 26, as can be seen from FIG.
  • a plurality of stiffening beads 67 are arranged on the top 37 of the dome-like piston pin support chair 15 and are distributed around the circumference.
  • the annular support collar 14 has at its upper end such a diameter that it supports the piston upper part 2 lying on its annular contact surface 13 in its bending-neutral zone.
  • those peripheral areas of the lower edge 68 of the piston lower part 1 are generally formed as oil-scraper edges 69 in the area axially below the two openings 65 and 66 in the outer wall 21, as can be seen in FIG. 2, while the remaining areas in the area of the pressure and the circumferential regions of the lower edge 68 of the lower piston part 1 lying on the counterpressure side of the plunger are chamfered or rounded as oil delivery surfaces 70.
  • This special design of the lower edge 68 on the lower piston part 1 ensures that in the region of the pressure side and the counter-pressure side of the plunger there is always a sufficient lubricating film between the cylindrical outer surface 71 of the lower piston part 1 and the associated cylinder wall, which is ensured by the oil delivery surfaces 70, while in the remaining circumferential areas of the plunger, namely the areas below the openings 65 and 66, in which significantly less lubricating oil is naturally required, the lubricating oil film adhering to the cylinder wall is reduced to a minimum film thickness by the sharp-edged oil wiping edges 69 when the piston is moving downward. This results in a significant reduction in oil consumption in machine operation.
  • the radius of the outer boundary surface 72 adjacent to the outer contour 62 of the connecting rod head 34 is preferably, as can be seen from FIG. 1, somewhat larger than the radius of the outer contour 62 of the connecting rod head 34.
  • the entry region of the cooling oil passage hole 39 is conical to the connecting rod head 34 expanded. This ensures a perfect transfer of the cooling oil leaving the spray bore 48 in the connecting rod head 26 into the cooling oil passage hole 39 and a favorable transfer of the cooling oil through the latter into the inner cooling space 41.
  • the outer wall 4 on the upper piston part 2 and the outer wall 21 on the lower piston part 1 in the plunger piston according to FIGS. 1 to 3 are preferably matched in their height so that after connecting the upper piston part 2 and lower piston part 1 between the flat lower edge 73 of the outer wall 4 of the upper piston part 2 and the flat upper edge 74 of the outer wall 21 of the lower piston part 1, an annular gap 75 remains free, through which oil from the bottom, which is arranged on the upper piston part 2 of the piston rings 6 from the cylinder wall, can enter the outer cooling space 45.
  • the dome-shaped piston-piston carrying chair 15 is - as can be seen from FIG. 1 - connected to the outer wall 21 of the piston lower part 1 approximately at the level of a piston transverse plane containing the piston pin longitudinal axis.
  • the features according to the invention and in particular their combinatorial combination in a plunger ensure that the plunger can function properly even at the highest ignition pressures of the order of 180 bar, for example.
  • the piston upper part 2 in a bending-neutral zone in connection with the dome-like design of the piston pin support, chair 15 and the dome-like limitation of the inner cooling space 41, it is ensured that the ignition pressures acting on the plunger in machine operation in the best possible way via the support collar 14 and the piston pin 76 can be introduced into the connecting rod 33 in such a way that the cylindricity and coaxiality of the outer wall 4 of the upper piston part 2 and the outer wall 21 of the lower piston part 1 are largely preserved.
  • the cooling oil guide in particular in the upper piston part 2, also ensures intensive cooling of the same. Negative influences from the temperatures prevailing in machine operation on the shape of the piston upper part 2 can therefore also be largely avoided by the type of coolant guidance in the piston upper part.

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  • 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)
EP86100309A 1985-01-26 1986-01-11 Piston à plusieurs parties, refroidi par de l'huile, pour moteurs à combustion interne à piston alternatif Expired EP0189767B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19853502644 DE3502644A1 (de) 1985-01-26 1985-01-26 Oelgekuehlter, mehrteiliger tauchkolben fuer hubkolbenbrennkraftmaschinen
DE3502644 1985-01-26

Publications (3)

Publication Number Publication Date
EP0189767A2 true EP0189767A2 (fr) 1986-08-06
EP0189767A3 EP0189767A3 (en) 1987-04-01
EP0189767B1 EP0189767B1 (fr) 1988-08-10

Family

ID=6260869

Family Applications (1)

Application Number Title Priority Date Filing Date
EP86100309A Expired EP0189767B1 (fr) 1985-01-26 1986-01-11 Piston à plusieurs parties, refroidi par de l'huile, pour moteurs à combustion interne à piston alternatif

Country Status (5)

Country Link
EP (1) EP0189767B1 (fr)
JP (1) JP2540493B2 (fr)
DE (2) DE3502644A1 (fr)
FI (1) FI79888B (fr)
NO (1) NO163153C (fr)

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0464626A1 (fr) * 1990-06-29 1992-01-08 KOLBENSCHMIDT Aktiengesellschaft Piston assemblé refroidi par huile pour moteur diesel
EP0520536B1 (fr) * 1991-06-25 1997-04-09 KOLBENSCHMIDT Aktiengesellschaft Piston assemblé refroidi par huile pour moteur Diesel
EP0787898A1 (fr) * 1996-02-01 1997-08-06 KOLBENSCHMIDT Aktiengesellschaft Piston articulé en plusieurs parties
US9127618B2 (en) 2012-09-27 2015-09-08 Federal-Mogul Corporation Reduced compression height piston and piston assembly therewith and methods of construction thereof
EP3208453A1 (fr) * 2016-02-18 2017-08-23 MAN Truck & Bus AG Piston pour un moteur à combustion interne alternatif
US10184422B2 (en) 2014-12-30 2019-01-22 Tenneco Inc. Reduced compression height dual gallery piston, piston assembly therewith and methods of construction thereof
US10294887B2 (en) 2015-11-18 2019-05-21 Tenneco Inc. Piston providing for reduced heat loss using cooling media
US20200080587A1 (en) * 2018-09-12 2020-03-12 Pai Industries, Inc. Forged Steel Cross-Head Piston
CN115492694A (zh) * 2022-09-14 2022-12-20 重庆潍柴发动机有限公司 振荡冷却活塞

Families Citing this family (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3511835A1 (de) * 1985-03-30 1986-10-09 M.A.N.- B & W Diesel GmbH, 8900 Augsburg Oelgekuehlter tauchkolben einer brennkraftmaschine
DE3518721C3 (de) * 1985-05-24 1997-09-04 Man B & W Diesel Ag Ölgekühlter, mehrteiliger Tauchkolben einer Brennkraftmaschine
DE3707462A1 (de) * 1987-03-07 1988-09-15 Man B & W Diesel Gmbh Oelgekuehlter, mehrteiliger tauchkolben fuer brennkraftmaschinen
DE3723046A1 (de) * 1987-07-11 1989-01-19 Man B & W Diesel Gmbh Tauchkolben einer hubkolbenbrennkraftmaschine
DE3832022C1 (fr) * 1988-09-21 1989-09-21 Mahle Gmbh, 7000 Stuttgart, De
DE4040611A1 (de) * 1990-12-19 1992-07-02 Man B & W Diesel Ag Jet-kolbenkuehlung
ES2266011T3 (es) † 1999-10-08 2007-03-01 Federal-Mogul Corporation Piston con doble galeria.
DE102005048981B4 (de) 2005-10-13 2010-04-29 Man B & W Diesel A/S Kolben für einen Kreuzkopfmotor
DE102012207951B4 (de) * 2012-05-11 2022-09-22 Man Energy Solutions Se Kolben einer Brennkraftmaschine
DE102012017217A1 (de) 2012-08-31 2014-05-15 Mahle International Gmbh Kolben für einen Verbrennungsmotor
DE102013002232B4 (de) * 2013-02-11 2022-11-17 Man Energy Solutions Se Kolben einer Brennkraftmaschine
DE102017201137A1 (de) 2017-01-25 2018-07-26 Volkswagen Aktiengesellschaft Kolben für einen Verbrennungsmotor

Family Cites Families (23)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE7203513U (de) * 1972-05-10 Alcan Alu-Werke Gmbh Mehrteiliger Kolben mit Kühlraum im Kolbenkopf
CH75489A (de) * 1917-01-09 1917-08-01 A Riedler Ölsparvorrichtung an Kolbenmaschinen
AT141390B (de) * 1932-10-25 1935-04-10 Ernst Dipl Ing Mahle Leichtmetallkolben für Brennkraftmaschinen.
CH196752A (de) * 1937-03-23 1938-03-31 Sulzer Ag Gekühlter Kolben für Brennkraftmaschinen.
DE961847C (de) * 1944-05-24 1957-04-11 Schmidt Gmbh Karl Kolben fuer Brennkraftmaschinen
DE1006669B (de) * 1953-06-16 1957-04-18 Maybach Motorenbau Gmbh Mehrteiliger, oelgekuehlter Kolben fuer eine Brennkraftmaschine
JPS4212887Y1 (fr) * 1964-10-12 1967-07-21
DE1526598A1 (de) * 1966-10-07 1970-02-12 Maschf Augsburg Nuernberg Ag Einrichtung zur Verringerung des Zylinderbuechsenverschleisses bei Tauchkolbenmotoren insbesondere fuer Schweroelbetrieb
GB1232990A (fr) * 1967-09-28 1971-05-26
FR2079873A5 (fr) * 1970-02-16 1971-11-12 Semt
DE2140824C2 (de) * 1971-08-14 1983-06-01 M.A.N. Maschinenfabrik Augsburg-Nürnberg AG, 8900 Augsburg Ölgekühlter Kolben für Brennkraftmaschinen
DE2307347A1 (de) * 1973-02-15 1974-08-22 Maschf Augsburg Nuernberg Ag Mehrteiliger tauchkolben fuer viertaktbrennkraftmaschinen, insbesondere grossdieselmotoren
JPS5179239U (fr) * 1975-11-26 1976-06-23
JPS52141538U (fr) * 1976-04-23 1977-10-26
JPS52130011A (en) * 1976-04-24 1977-11-01 Sanwa Seiki Mfg Co Ltd Positive displacement engines
JPS5416975U (fr) * 1977-07-08 1979-02-03
DE2919638A1 (de) * 1979-05-16 1980-11-20 Schmidt Gmbh Karl Kolben fuer brennkraftmaschinen
JPS5633575A (en) * 1979-08-25 1981-04-04 Nissan Motor Co Ltd Ground speed detecting rader for vehicle
JPS5831464A (ja) * 1981-08-19 1983-02-24 Fujitsu Ltd ジョブ出力情報の伝送方式
JPS58186122U (ja) * 1982-06-04 1983-12-10 株式会社小松製作所 ピストンク−リングノズル
JPS5924853U (ja) * 1982-08-09 1984-02-16 旭化成株式会社 収納ボツクス
DE3303984C1 (de) * 1983-02-05 1984-05-24 Mahle Gmbh, 7000 Stuttgart Mehrteiliger,fluessigkeitsgekuehlter Kolben fuer Verbrennungsmotoren
JPS59181248U (ja) * 1983-05-20 1984-12-03 川崎重工業株式会社 内燃機関のピストン装置

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0464626A1 (fr) * 1990-06-29 1992-01-08 KOLBENSCHMIDT Aktiengesellschaft Piston assemblé refroidi par huile pour moteur diesel
EP0520536B1 (fr) * 1991-06-25 1997-04-09 KOLBENSCHMIDT Aktiengesellschaft Piston assemblé refroidi par huile pour moteur Diesel
EP0787898A1 (fr) * 1996-02-01 1997-08-06 KOLBENSCHMIDT Aktiengesellschaft Piston articulé en plusieurs parties
US9127618B2 (en) 2012-09-27 2015-09-08 Federal-Mogul Corporation Reduced compression height piston and piston assembly therewith and methods of construction thereof
US10184422B2 (en) 2014-12-30 2019-01-22 Tenneco Inc. Reduced compression height dual gallery piston, piston assembly therewith and methods of construction thereof
US10294887B2 (en) 2015-11-18 2019-05-21 Tenneco Inc. Piston providing for reduced heat loss using cooling media
EP3208453A1 (fr) * 2016-02-18 2017-08-23 MAN Truck & Bus AG Piston pour un moteur à combustion interne alternatif
US10502158B2 (en) 2016-02-18 2019-12-10 Man Truck & Bus Ag Piston for a reciprocating-piston internal combustion engine
US20200080587A1 (en) * 2018-09-12 2020-03-12 Pai Industries, Inc. Forged Steel Cross-Head Piston
CN115492694A (zh) * 2022-09-14 2022-12-20 重庆潍柴发动机有限公司 振荡冷却活塞

Also Published As

Publication number Publication date
FI79888B (fi) 1989-11-30
NO860264L (no) 1986-07-28
NO163153B (no) 1990-01-02
EP0189767B1 (fr) 1988-08-10
JP2540493B2 (ja) 1996-10-02
JPS61175256A (ja) 1986-08-06
DE3502644A1 (de) 1986-07-31
FI854870A7 (fi) 1986-07-27
EP0189767A3 (en) 1987-04-01
NO163153C (no) 1990-04-11
FI854870A0 (fi) 1985-12-10
DE3660506D1 (en) 1988-09-15

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