EP3301284B1 - Kolben mit anordnung zur kühlung - Google Patents

Kolben mit anordnung zur kühlung Download PDF

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Publication number
EP3301284B1
EP3301284B1 EP16191417.1A EP16191417A EP3301284B1 EP 3301284 B1 EP3301284 B1 EP 3301284B1 EP 16191417 A EP16191417 A EP 16191417A EP 3301284 B1 EP3301284 B1 EP 3301284B1
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EP
European Patent Office
Prior art keywords
piston
cooling
lubricant
plenum
passage
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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.)
Active
Application number
EP16191417.1A
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English (en)
French (fr)
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EP3301284A1 (de
Inventor
Matthias Veltmann
Karl Stellwagen
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Caterpillar Energy Solutions GmbH
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Caterpillar Energy Solutions GmbH
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Priority to EP16191417.1A priority Critical patent/EP3301284B1/de
Publication of EP3301284A1 publication Critical patent/EP3301284A1/de
Application granted granted Critical
Publication of EP3301284B1 publication Critical patent/EP3301284B1/de
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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
    • 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

Definitions

  • the present disclosure generally relates to a piston for an engine, in particular, to a piston with a cooling arrangement for cooling the same during operation of the engine.
  • pistons of engines are configured to reciprocate within a cylinder liner of a cylinder.
  • Lubricant between an inner circumference of the cylinder liner and an outer circumference (also referred to as piston skirt) of the piston facilitates lubrication and cooling of the piston and the cylinder liner during operation of the engine.
  • US 4,577,595 discloses a piston for a reciprocating piston internal combustion engine including an annular cooling oil space which is supplied with cooling oil by way of an oil collecting device.
  • the cooling oil can flow off toward a piston center by way of bores.
  • DE 10 2015 215 482 A1 discloses a piston for an internal combustion engine having a cooling passage in which a separation element having at least one opening is positioned. Oil is continuously sprayed into the cooling passage via the opening.
  • FR 2 582 351 A1 discloses another piston for an internal combustion engine with oil cooling.
  • US 4 587 932 A discloses a composite piston for internal combustion engines with an interior cooling chamber and an outer cooling passage.
  • EP 0 064 831 A2 discloses a piston crown for an internal combustion engine.
  • FR 2 125 687 A5 discloses another piston for an internal combustion engine.
  • the present disclosure is directed, at least in part, to improving or overcoming one or more aspects of prior systems.
  • a piston for an engine comprises a piston body having a longitudinal axis. At least one piston ring groove is formed in an outer peripheral wall of the piston body. An outer plenum is formed inside the piston body adjacent to the outer peripheral wall at a position corresponding to the at least one piston ring groove.
  • a cooling inlet is configured to receive lubricant for cooling the piston body.
  • At least one cooling passage is configured to receive lubricant supplied from the cooling inlet and supply the received lubricant to the outer plenum.
  • the at least one cooling passage extends towards the outer peripheral wall at an upwardly-inclined angle with respect to the longitudinal axis and opens into the outer plenum.
  • an engine comprises at least one cylinder and an at least one piston as exemplarily disclosed herein, the piston being adapted to reciprocate within the at least one cylinder.
  • the present disclosure may be based in part on the realization that cooling of the piston and the piston rings is crucial in terms of robust engine operation.
  • the region adjacent to an uppermost piston ring has to be maintained below a certain temperature level. Otherwise, coke from decomposing lube oil may form and accumulate in the crevices between the piston ring and the piston, eventually causing immobility of the ring and subsequent damage to the piston and the cylinder liner.
  • the present disclosure may be based at least in part on the realization that, when lube oil is supplied to a set of plenums and ducts inside a piston to transfer heat from critical regions to the lube oil, the lube oil will accumulate at the top of the plenums or ducts when the piston is moving downward. During this time, while the lube oil will be in contact with those regions of the piston that are important with respect to cooling, it has been recognized that the heat transfer from the piston to the lube oil is dependent on the lube oil motion on the surface to be cooled. In other words, when the lube oil flows along the surface to be cooled, more energy per unit area and unit time can be transferred compared to a non-flowing lube oil. Therefore, it has been realized that it is preferred to perform cooling by forced convection of the lube oil such that the lube oil flows along the surfaces to be cooled for enhanced cooling.
  • a continuous lube oil flow adjacent to the critical regions to be cooled can be obtained by utilizing an oil distribution passage that distributes oil to a plurality of transfer passages that are equally spread out along the circumference of the piston.
  • a forced convection of the lube oil is achieved by an orientation of the transfer passages according to which the transfer passages provide the lube oil to an outer plenum of the piston under a slight angle, i.e., the transfer passages are upwardly-inclined with respect to the longitudinal axis of the piston.
  • the present disclosure may further be based on the realization that it may be advantageous to maintain a minimum lube oil level in the piston at all times. This provides an improved initial cooling due to oil remaining in the piston splashing against the upper region of the plenum when the piston is decelerating upon reaching the top dead center. It has been realized that this may be achieved by providing raised outlet passages at the bottom of the plenum, such that part of the lube oil in the plenum is prevented from leaving the plenum during the upward motion of the piston.
  • cooling of the piston top may be adjusted in an appropriate manner by optimizing the lube oil distribution system, e.g., the volume of the distribution passage, the cross-sectional area of the same, the orientation and position of the transfer passages, and the like. Further, it has been realized that the volume of lube oil that is held in the distribution passage can be adjusted by providing raised inlets that are disposed above the lowest surface of the distribution passage. Accordingly, part of the lube oil will remain in the distribution passage as the piston moves upward.
  • the lube oil distribution system e.g., the volume of the distribution passage, the cross-sectional area of the same, the orientation and position of the transfer passages, and the like.
  • the present disclosure may be based at least in part on the realization that it may be advantageous to increase the flow velocity of the lube oil in the distribution passage away from the position of the inlet to achieve a substantially constant mass flow along the circumference of the distribution passage such that each transfer passage receives substantially the same amount of lube oil during operation of the engine.
  • a piston as exemplarily disclosed herein may be used in internal combustion engines, compressors, pumps and other machines comprising a piston with at least one piston ring groove and a piston ring (hereinafter referred to generally as engines).
  • engines a piston with at least one piston ring groove and a piston ring
  • an exemplary piston is described in connection with an internal combustion engine in the following.
  • an exemplary engine 100 includes an engine block 101 that at least partially defines a plurality of cylinders 102, a piston 1 slidably disposed within each cylinder 102, and a cylinder head 104 associated with each cylinder 102.
  • Engine 100 further includes a plurality of inlet valves 106 and exhaust valves 108 associated with the plurality of cylinders 102, as well as an actuating mechanism 112 connected to, e.g., a cam shaft 114 of engine 100.
  • Engine 100 may include features not shown, such as fuel systems, air systems, cooling systems, peripheries, drivetrain components, etc.
  • engine 100 may be of any size, with any number of cylinders, and in any configuration ("V", in-line, radial, etc.).
  • Engine 100 may be used to power any machine or other device, including locomotive applications, on-highway trucks or vehicles, off-highway trucks or machines, earth moving equipment, generators, aerospace applications, marine applications, pumps, stationary equipment, or other engine-powered applications, and run on any type of fuel, including gaseous fuel, gasoline, diesel, heavy fuel oil, etc.
  • Piston 1 and cylinder liner 2 may be arranged within engine block 101 of engine 100.
  • Piston 1 comprises a central longitudinal axis 3. Furthermore, piston 1 comprises a piston body 4 with a piston skirt 6, a piston top 8, and a plurality of piston rings. Piston 1 is connected via a piston rod 9 to a crankshaft (not shown) of the internal combustion engine, and is adapted to reciprocate in cylinder liner 2 during operation of the internal combustion engine.
  • Piston top 8 defines a combustion chamber 11 together with cylinder liner 2 and a cylinder head (not shown).
  • Piston skirt 6 defines an outer circumference of piston body 4.
  • a plurality of piston ring grooves extends circumferentially around piston body 4 in piston skirt 6.
  • an upper piston ring groove 10 an intermediate piston ring groove 12 and a lower piston ring groove 14 are arranged in piston skirt 6.
  • the lower piston ring groove 14 is arranged farthest from piston top 8 compared to the other piston ring grooves.
  • lower piston ring groove 14 is the lowermost piston ring groove
  • upper piston ring groove 10 is the uppermost piston ring groove.
  • Each of a plurality of piston rings is arranged in a corresponding piston ring groove.
  • a compression ring 16 is arranged in upper piston ring groove 10
  • an intermediate ring 18 is arranged in intermediate piston ring groove 12
  • an oil scraper ring 20 is arranged in lower piston ring groove 14.
  • Piston 1 further comprises a cooling arrangement configured to cool piston 1, in particular, piston top 8 and the region adjacent to piston ring grooves 10, 12, 14, which will be described in more detail below with reference to Fig. 3 .
  • a piston may comprise a different number of piston ring grooves and corresponding piston rings than shown in Figs. 1 and 2 .
  • an engine may comprise at least one cylinder, each cylinder having a piston as exemplarily disclosed herein.
  • Each piston may be adapted to reciprocate within a corresponding cylinder.
  • FIG. 3 a cross-sectional view of a piston with a cooling arrangement in accordance with the present disclosure is shown.
  • piston 1 includes an arrangement of passages and plenums within the same to circulate a lubricant such as lube oil during the reciprocating movement of piston 1 in the associated cylinder.
  • plenum refers to chambers or cavities (spaces) formed in piston body 4, to which lubricant is supplied to cool piston 1.
  • an outer plenum 22 is formed inside piston body 4 adjacent to an outer peripheral wall 5 of piston skirt 6 at a position corresponding to piston ring grooves 10, 12, 14.
  • a central plenum 28 is formed at a center of piston body 4 and separated from outer plenum 22 by an annular partition wall 30.
  • plenums 22, 28 During downward movement of piston 1, lubricant accumulates in the upper region of plenums 22, 28 to cool the adjacent regions of piston 1, in particular, the regions adjacent to piston ring grooves 10, 12, 14 and a bottom 32 of a piston bowl 34 formed in piston top 8, as shown by the dashed line in Fig. 3 .
  • the configuration of plenums 22, 28 is symmetrical, i.e. central plenum 28 is symmetrical with respect to longitudinal axis 3, and outer plenum 22 is an annular space extending around longitudinal axis 3 in the circumferential direction. It will be readily appreciated that, in other embodiments, different configurations of plenums 22, 28 may be used without departing from the present teachings.
  • Piston 1 further comprises at least one cooling inlet (duct or passage) 24 configured to receive lubricant for cooling piston body 4.
  • cooling inlet 24 is a passage that is provided in annular partition wall 30 and extends along longitudinal axis 3, i.e., vertically. More precisely, an opening of cooling inlet 24 is provided in a lower surface of annular partition wall 30 and receives lubricant that is sprayed upwards from a cooling nozzle (not shown) disposed below piston 1 at a position that corresponds to cooling inlet 24.
  • a single cooling inlet 24 is shown in Fig. 3 , it will be appreciated that any appropriate number of cooling inlets 24 may be provided and arranged along the circumferential direction of piston 1, for example, with equal distances from each other. Likewise, a corresponding number of cooling nozzles, for example, two cooling nozzles for two cooling inlets, may be provided.
  • lubricant entering cooling inlet 24 flows through the same and reaches a circumferentially extending lubricant distribution passage 36.
  • lubricant distribution passage 36 is formed as an annular space or cavity within annular partition wall 30 that extends in the circumferential direction.
  • Lubricant distribution passage 36 is configured to distribute the lubricant entering via the one or more cooling inlets 24 in the circumferential direction.
  • a plurality of cooling intermediate passages 38 are fluidly connected to lubricant distribution passage 36 and extend therefrom to a corresponding plurality of cooling passages 26 formed in annular partition wall 30 to fluidly connect central plenum 28 to outer plenum 22.
  • each cooling intermediate passage 38 extends along longitudinal axis 3, i.e., vertically, from lubricant distribution passage 36.
  • the plurality of cooling passages 26 and the associated cooling intermediate passages 38 are equidistantly arranged in the circumferential direction. It should be noted that, while it is shown in Fig. 3 that cooling intermediate passage 38 is aligned with cooling inlet 24 in the circumferential direction, in other embodiments, cooling intermediate passage(s) 38 may be arranged at a position that is different from that of cooling inlet(s) 24.
  • Lubricant that has been distributed by lubricant distribution passage 36 enters cooling passages 26 via cooling intermediate passage 38.
  • Cooling passage 26 extends from central plenum 28 to outer plenum 22 at an upwardly-inclined angle of less than 90 degrees with respect to longitudinal axis 3, for example, an angle of between 0° and 45°, preferably between 15° and 30°, or an angle of between 45° and 90°, preferably between 60° and 75°.
  • lubricant entering cooling passage 26 via cooling intermediate passage 38 is imparted with a flow velocity component directed along cooling passage 26 upon entering central plenum 28 and outer plenum 22. Accordingly, upon entering central plenum 28 and outer plenum 22, the lubricant flows along the inner surfaces of the same in a manner that is shown by the flow lines in Fig. 3 .
  • cooling passage 26 is particularly advantageous for outer plenum 22, because it facilitates the flow of lubricant to outer plenum 22 as piston 1 is moving downward. Therefore, by arranging cooling passage 26 as shown in Fig. 3 , cooling of the critical regions of piston 1, in particular, the region adjacent to piston ring grooves 10, 12, 14 can be increased.
  • cooling passage 26 may have a different configuration.
  • cooling passage 26 may extend at an upwardly-inclined angle from the opening of cooling intermediate passage 38 towards outer plenum 22, and may extend at a different angle towards central plenum 28, for example, substantially horizontally, or also at an upwardly-inclined angle.
  • a central lubricant outlet 40 is formed at the center of a bottom 41 of central plenum 28 and includes a central opening 42 that is opened towards an inside of central plenum 28.
  • a peripheral lubricant outlet 44 more precisely, a plurality of peripheral lubricant outlets 44, are fluidly connected to outer plenum 22 for discharging the lubricant from outer plenum 22 towards a lower end of piston body 4.
  • each peripheral lubricant outlet 44 is configured as a tube-like member 46, for example, made of metal, that is inserted into a bore formed in piston body 4 to extend along longitudinal axis 3.
  • peripheral lubricant outlet 44 projects into outer plenum 22 such that an inlet opening of the same is disposed above a lowest portion (bottom surface) of outer plenum 22.
  • peripheral lubricant outlet 44 projects into outer plenum 22 such that an inlet opening of the same is disposed above a lowest portion (bottom surface) of outer plenum 22.
  • central opening 42 of lubricant outlet 40 may be disposed above bottom 41 of central plenum 28.
  • cooling inlet 24 may have an outlet opening into lubricant distribution passage 36, said outlet being arranged above a lowest portion of lubricant distribution passage 36. In this manner, part of the lubricant in lubricant distribution passage 36 remains in the same during upward movement of piston 1, and may be supplied to cooling intermediate passages 38 and cooling passages 26 during the subsequent downward movement of piston 1.
  • a velocity of lubricant towards cooling passages 26 decreases with increasing distance from cooling inlet 24 in case lubricant distribution passage 36 has a constant cross-section. Therefore, in order to assure that the velocity of the lubricant flowing through lubricant distribution passage 36 remains substantially constant, a cross-section of the same may be varied. In particular, the cross-section of lubricant distribution passage 36 may decrease away from cooling inlet 24. For example, a bottom of lubricant distribution passage 36 may be raised as lubricant distribution passage 36 extends away from cooling inlet 24.
  • lubricant distribution passage 36 may have a downward slope away from cooling inlet 24, which may result in an increasing cross-section of the same, to enhance oil flow to cooling passages 26 as piston 1 approaches top dead center.
  • piston 1 reciprocates in cylinder liner 2. Specifically, piston 1 reciprocates between a top dead centre (TDC) and a bottom top centre (BDC) in cylinder liner 2. As known by those skilled in the art, a velocity of piston 1 is constantly changing during upstroke and downstroke. For example, piston 1 decelerates before arriving at TDC and BDC, respectively.
  • TDC top dead centre
  • BDC bottom top centre
  • lubricant is supplied to the same from a plurality of cooling nozzles ejecting lubricant into piston body 4.
  • the position and the number of the cooling nozzles may correspond to the position and the number of cooling inlets 24 formed in piston body 4. Accordingly, as piston 1 moves downward within cylinder liner 2, lubricant enters cooling inlet 24. The lubricant then flows into lubricant distribution passage 36 to be distributed along the circumference of piston 1. Via the plurality of cooling intermediate passages 38, lubricant enters the plurality of cooling passages 26, which are equidistantly arranged in the circumferential direction.
  • a cooling efficiency of critical regions of piston body 4, in particular, outer peripheral wall 5 comprising piston ring grooves 10, 12, 14, can be increased due to the increased heat transfer of the lubricant that is flowing along the inner surface of outer plenum 22.

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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)

Claims (12)

  1. Kolben (1) für einen Motor (100), wobei der Kolben (1) umfasst:
    einen Kolbenkörper (4), der eine Längsachse (3) aufweist;
    mindestens eine Kolbenringnut (10, 12, 14), die in einer Außenumfangswand (5) des Kolbenkörpers (4) gebildet ist;
    eine äußere Kammer (22), die innerhalb des Kolbenkörpers (4) angrenzend an die Außenumfangswand (5) an einer Position gebildet ist, die der mindestens einen Kolbenringnut (10, 12, 14) entspricht;
    eine zentrale Kammer (28), die in einer Mitte des Kolbenkörpers (4) gebildet ist, wobei die zentrale Kammer (28) von der äußeren Kammer (22) durch eine Trennwand (30), zum Beispiel eine ringförmige Trennwand (3), getrennt ist;
    einen Kühleinlass (24), der konfiguriert ist, um Schmiermittel zum Kühlen des Kolbenkörpers (4) aufzunehmen; und
    mindestens einen Kühlkanal (26), der in der Trennwand (30) gebildet ist und sich zwischen der zentralen Kammer (28) und der äußeren Kammer (22) erstreckt, wobei der mindestens eine Kühlkanal (26) konfiguriert ist, um Schmiermittel aufzunehmen, das vom Kühleinlass (24) zugeführt wird, und das aufgenommene Schmiermittel der äußeren Kammer (22) zuzuführen,
    wobei sich der mindestens eine Kühlkanal (26) in Bezug auf die Längsachse (3) in einem nach oben geneigten Winkel in Richtung der Außenumfangswand (5) erstreckt und sich in die äußere Kammer (22) öffnet und
    dadurch gekennzeichnet, dass der Kühleinlass (24) in der Trennwand (30) vorzugsweise als parallel zur Längsachse (3) verlaufender Kanal gebildet ist.
  2. Kolben (1) nach Anspruch 1, ferner umfassend einen sich in Umfangsrichtung erstreckenden Schmiermittelverteilungskanal (36), der fluidisch mit dem Kühleinlass (24) verbunden ist, wobei der mindestens eine Kühlkanal (26) durch mindestens einen entsprechenden Kühlzwischenkanal (38), der in der ringförmigen Trennwand (30) gebildet ist, fluidisch mit dem Schmiermittelverteilungskanal (36) verbunden ist.
  3. Kolben (1) nach Anspruch 2, umfassend eine Vielzahl von Kühlkanälen (26) und eine Vielzahl entsprechender Kühlzwischenkanäle (38), wobei die Vielzahl von Kühlkanälen (26) und die Vielzahl von Kühlzwischenkanälen (26) äquidistant in der Umfangsrichtung angeordnet sind.
  4. Kolben (1) nach Anspruch 2 oder 3, wobei der Kühleinlass (24) einen Auslass aufweist, der sich in den Schmiermittelverteilungskanal (36) öffnet, wobei der Auslass oberhalb eines untersten Abschnitts des Schmiermittelverteilungskanals (36) angeordnet ist.
  5. Kolben (1) nach einem der Ansprüche 2 bis 4, wobei sich der Schmiermittelverteilungskanal (36) in Umfangsrichtung mit variierendem Querschnitt erstreckt, vorzugsweise mit einem Querschnitt, der sich vom Kühleinlass (24) weg verringert.
  6. Kolben (1) nach einem der Ansprüche 1 bis 5, wobei die zentrale Kammer (28) einen Schmiermittelauslass (40) einschließt, der in einer Mitte eines Bodens (41) der zentralen Kammer (28) gebildet ist.
  7. Kolben (1) nach Anspruch 6, wobei der Schmiermittelauslass (40) eine zentrale Öffnung (42) einschließt, die über dem Boden (41) angeordnet ist.
  8. Kolben (1) nach einem der Ansprüche 1 bis 7, ferner umfassend einen peripheren Schmiermittelauslass (44), der fluidisch mit der äußeren Kammer (22) verbunden ist, um Schmiermittel aus der äußeren Kammer (22) in Richtung eines unteren Endes des Kolbenkörpers (4) abzugeben.
  9. Kolben (1) nach Anspruch 8, wobei der periphere Schmiermittelauslass (44) derart in die äußere Kammer (22) hineinragt, dass eine Einlassöffnung davon oberhalb eines untersten Abschnitts der äußeren Kammer (22) angeordnet ist.
  10. Kolben (1) nach Anspruch 9, wobei der periphere Schmiermittelauslass (44) als ein rohrartiges Element (46) konfiguriert ist, zum Beispiel aus Metall, das in eine Bohrung eingesetzt ist, die im Kolbenkörper (4) gebildet ist.
  11. Kolben (1) nach einem der Ansprüche 1 bis 10, wobei sich der mindestens eine Kühlkanal (26) in Bezug auf die Längsachse (3) in einem nach oben geneigten Winkel von weniger als 90 Grad, zum Beispiel zwischen 0° und 45°, vorzugsweise zwischen 15° und 30° oder zwischen 45° und 90°, vorzugsweise zwischen 60° und 75°, in Richtung der Außenumfangswand (5) erstreckt.
  12. Motor (100), umfassend:
    mindestens einen Zylinder (102) und
    mindestens einen Kolben (1) nach einem der Ansprüche 1 bis 11, der ausgelegt ist, sich innerhalb des mindestens einen Zylinders (102) hin- und herzubewegen.
EP16191417.1A 2016-09-29 2016-09-29 Kolben mit anordnung zur kühlung Active EP3301284B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP16191417.1A EP3301284B1 (de) 2016-09-29 2016-09-29 Kolben mit anordnung zur kühlung

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP16191417.1A EP3301284B1 (de) 2016-09-29 2016-09-29 Kolben mit anordnung zur kühlung

Publications (2)

Publication Number Publication Date
EP3301284A1 EP3301284A1 (de) 2018-04-04
EP3301284B1 true EP3301284B1 (de) 2020-11-25

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Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN116412038B (zh) * 2022-10-19 2026-04-07 中国船舶集团有限公司第七一一研究所 一种活塞顶、活塞裙部及组合活塞

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2125687A5 (de) * 1971-02-16 1972-09-29 Semt
JPS57178150U (de) * 1981-05-07 1982-11-11
DE3338419A1 (de) 1983-10-22 1985-05-02 Mtu Motoren- Und Turbinen-Union Friedrichshafen Gmbh, 7990 Friedrichshafen Kolben fuer eine hubkolbenbrennkraftmaschine
DE3403624A1 (de) * 1984-02-02 1985-08-08 Kolbenschmidt AG, 7107 Neckarsulm Gebauter, fluessigkeitsgekuehlter kolben fuer brennkraftmaschinen
DE3518721C3 (de) * 1985-05-24 1997-09-04 Man B & W Diesel Ag Ölgekühlter, mehrteiliger Tauchkolben einer Brennkraftmaschine
PL3129629T3 (pl) * 2014-04-09 2018-11-30 Ks Kolbenschmidt Gmbh Przedłużony dopływ kanału chłodzenia dla tłoków z kanałem chłodzenia i sposób jego działania
EP3180505A1 (de) * 2014-08-15 2017-06-21 KS Kolbenschmidt GmbH Kühlölring

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

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