EP3070280B1 - Shell system for a machine housing structure for a combustion engine - Google Patents

Shell system for a machine housing structure for a combustion engine Download PDF

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Publication number
EP3070280B1
EP3070280B1 EP16000593.0A EP16000593A EP3070280B1 EP 3070280 B1 EP3070280 B1 EP 3070280B1 EP 16000593 A EP16000593 A EP 16000593A EP 3070280 B1 EP3070280 B1 EP 3070280B1
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EP
European Patent Office
Prior art keywords
pan
cooling ribs
upright walls
inner pan
ribs
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EP16000593.0A
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German (de)
French (fr)
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EP3070280A1 (en
Inventor
Claus Brüstle
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Neander Motors AG
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Neander Motors AG
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Classifications

    • 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
    • F01M11/00—Component parts, details or accessories, not provided for in, or of interest apart from, groups F01M1/00 - F01M9/00
    • F01M11/0004—Oilsumps
    • 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
    • F01M5/00—Heating, cooling, or controlling temperature of lubricant; Lubrication means facilitating engine starting
    • F01M5/002—Cooling
    • 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
    • F01M11/00—Component parts, details or accessories, not provided for in, or of interest apart from, groups F01M1/00 - F01M9/00
    • F01M11/0004—Oilsumps
    • F01M2011/0025—Oilsumps with heat exchangers
    • 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
    • F01M11/00—Component parts, details or accessories, not provided for in, or of interest apart from, groups F01M1/00 - F01M9/00
    • F01M11/0004—Oilsumps
    • F01M2011/0066—Oilsumps with passages in the wall, e.g. for axles or fluid passages
    • 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
    • F01M11/00—Component parts, details or accessories, not provided for in, or of interest apart from, groups F01M1/00 - F01M9/00
    • F01M11/0004—Oilsumps
    • F01M2011/0087—Sump being made of different parts
    • 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
    • F01M11/00—Component parts, details or accessories, not provided for in, or of interest apart from, groups F01M1/00 - F01M9/00
    • F01M11/04—Filling or draining lubricant of or from machines or engines
    • F01M11/0408—Sump drainage devices, e.g. valves, plugs
    • F01M2011/0416—Plugs

Definitions

  • the invention relates to a tray system for a machine housing structure of an internal combustion engine according to the preamble of patent claim 1.
  • EP 1 264 970 B1 There is an oil pan known EP 1 264 970 B1 , which is partially double-walled and has an inner shell made of plastic and an outer shell made of metal. In the space formed by the inner shell and the outer shell, a coolant for the lubricating oil receiving inner shell flows.
  • the inner shell has Abstützrippen, which bear against a bottom and upright walls of the inner shell. And on an outer side of a bottom of the outer shell cooling fins are provided.
  • a heat exchanger which influences the heat between coolant and ambient air, is integrated in the oil sump.
  • the FR 2 721 975 A1 is an oil pan again, which includes several cooling channels on its underside.
  • the cooling channels are connected to the cooling circuit of an internal combustion engine, and they are flowed through by the medium of the cooling circuit. Ribs are provided in the sump and cooling channels.
  • JP S63 75550 is treated a schematic internal combustion engine comprising a cylinder crankcase and an oil pan.
  • the latter two are composed in one plane.
  • the oil pan has an inner shell and an outer shell. Between them extends a channel for the circulation of the coolant of the internal combustion engine, which serves to influence the temperature of the lubricating oil in the oil pan. Between bottoms of the inner shell and the outer shell, an oil drain plug is provided.
  • the object of the invention is to conceive a trained for receiving by means of cooling liquid to be Entagindem lubricating oil pan system for an internal combustion engine, which is simple design, function optimized and easy to unite with a machine housing of the internal combustion engine.
  • the inner wall and the outer wall of the bathtub system can be represented with a defined design performance determination oriented.
  • the inner tub and the outer tub made of metal, preferably made of light metal and have an advantageous strength and thermal conductivity.
  • the particularly sophisticated cooling fin system especially on the ground and the upright walls of the inner wall, allows an optimized heat transfer between the coolant of the internal combustion engine acted upon inner trough and the lubricating oil of said internal combustion engine.
  • Emphasizing in this context is also the support system between the bottoms of the inner tub and the outer tub as well as the selected connection of the upright walls of the latter wells to the engine housing structure of the internal combustion engine.
  • the cooling fin system may also be provided on the outside of the upright walls of the inner tub.
  • the support system is exemplary constructed because it has a bearing pin owning a support pin at the bottom of the inner tub, which rests on a receiving socket of the bottom of the outer tub, wherein the bearing pin is in operative connection with a bore of the receiving socket.
  • the support system is extended by the fact that the bearing pin is provided with an oil drain plug.
  • free ends of the inner tub and the outer tub are designed as supports, which interact with counter-supports of a connection housing of the machine housing structure under a defined support load.
  • the latter solution is further optimized by the fact that the supports and the counter supports are delimited by a common plane between the inner tub and the outer tub or the connecting housing.
  • the fin system sets standards such that it includes a plurality of, for example, evenly distributed floor cooling fins on an inside of the floor and wall fins on an inside of the upright walls of the inner trough, which floor cooling fins and the wall fins are substantially perpendicular to the floor or upright walls Interior wall are aligned.
  • the particular efficiency of the cooling fin system contributes to the fact that at least one of the floor cooling fins extends over a defined partial height of an overall height of the upright walls of the inner trough. This is supported by the fact that the part height is e.g. is defined by the product 0.5 x total height of the upright walls of the inner tub.
  • improving the effect still has the effect that at least part of the wall cooling ribs extends approximately above the partial height of the floor cooling ribs and, on the other hand, that a first length of the wall cooling ribs on the outside of the upright walls of the inner tub is approximately 12 to 15 mm.
  • a second length of the wall cooling ribs on the outside of the inner tub also contribute that on the one hand a second length of the wall cooling fins on the inside of the upright walls of the inner tub by the factor 0.8 to 0.9 x the first Length and on the other hand, the distance between at least part of the floor cooling fins and the wall cooling fins is defined by the product 2 x second length of the wall cooling fins on the outside of the upright walls of the inner tub.
  • the thickness of at least part of the floor and wall cooling fins is between 1.5 and 2.5 mm.
  • An internal combustion engine 1 comprises a machine housing structure 2, which are essentially composed of a cylinder head and a cylinder crankcase-both are not shown.
  • the machine housing structure 2 is provided with a connection housing 3, to which a tub system 5 is connected.
  • the tub system 5 has a lubricating oil of the internal combustion engine receiving inner tub 6 and an outer tub 7, the trough-shaped and are set into each other and made of metal, preferably light metal.
  • the inner tub 6 has a bottom 8 and spaced upright walls 9 and 10; the outer tub 7 a bottom 11 and also spaced upright walls 12 and 13.
  • the floors 8 and 11, the walls 9 and 10 and 12 and 13 extend, for example, approximately at a parallel distance from each other, so that there is a gap 14 for the cooling liquid of the internal combustion engine 1 results, with the inner tub 6 and the lubricating oil contained therein is cooled.
  • This is supported by a cooling fin system 15, with which the inner tub 6, the tub system 5 is provided.
  • a support system 16 is provided between the inner tub 6 and the outer tub 7, which contributes to the constancy of the distances between the floors 8 and 11 and the upright walls 9 and 10 and 12 and 13.
  • the support system 16 which is only locally arranged in a vertical central longitudinal plane AA, comprises a bearing pin 17 made of one piece with the inner tub 6.
  • the bearing bolt 17 rests on a receiving bushing 21 of the base 11 with a collar 20 and protrudes into a bore with an integrally formed guide pin 22 23 of the receiving socket 21 into it.
  • an oil drain plug 24 is integrated in the guide pin 22.
  • Free ends 25, 26 and 27, 28 of the inner wall 6 and the outer tub 7 are formed as supports St1, St 2 and St 3, St 4, which with counter struts St5, St6 and St7, St8 of the connection housing 4 of the machine housing 3 by means of defined Support load act together, wherein between the supports St1, St2 and St3 and St4 and the counter supports St5, St6 and St7, St6 a seal 29 is provided.
  • the supports St 1, St 2 and St 3, St 4 and counter supports St 5, St 6 and St 7, St 8 are limited by an example.
  • an oil dipstick device 30 is arranged, of which a dipstick 31 encloses a defined, obtuse angle ⁇ to the transverse plane of the bath system 5.
  • the dipstick 31 dips into a lubricating oil volume Sv of the inner tub 6, which is delimited by an oil level Oes. So that the lubricating oil volume Sv is functionally cooled for the operation of the internal combustion engine 1, a cooling water volume Kv fed by a cooling water pump, not shown, of the internal combustion engine 1 is introduced into the intermediate space 14 of the bathtub system 5, which circulates the inner tub 7 in a cooling manner.
  • the cooling fin system 15 has on an inner side 32 of the bottom 8 of the inner tub 6 a plurality of e.g. evenly distributed floor cooling ribs 33 on. Also on the inside 32 of the inner tub 6, namely on the upright walls 9 and 10 wall cooling fins 34 and 35 are formed. Their arrangement corresponds essentially to that of the floor cooling fins 33. And both the floor cooling fins 33 and the wall cooling fins 34 and 35 are perpendicular to the bottom 8 and the upright walls 6 and 7 of the inner trough 6 aligned, the average thickness 36 of the latter ribs on their length measures about 1.5 to 2.5 mm.
  • At least a part of the bottom ribs 33 extends over a defined partial height Th of a total height Hges of the upright walls 9 and 10 of the inner tub 6 and of the tub system 5.
  • the partial height Th of the bottom cooling ribs 33 extends in the exemplary embodiment to near the oil level Oes of the lubricating oil volume Sv and she can be defined by the product 0.5 x total height Hges.
  • at least a portion of the wall cooling fins 34 and 35 extends in the direction of the transverse plane Qe, for example, approximately over the partial height Th of the floor cooling fins 33.
  • the fin system 15 comprises on an outer side 37 of the upright walls 9 and 10 of the inner tub 6 by wall cooling ribs 38 and 39.
  • a first length L1 of the wall cooling ribs 38 and 39 on the outside is about 12 to 15 mm; a second length L2 of the wall cooling fins 34 and 35 on the inside 32 of the inner tub 6 is formed by a factor of 0.8 to 0.9 x L1.
  • the distance As between at least part of the wall cooling fins 34 and 35 or 38 and 39 and the bottom cooling fins 33 is defined by the product 2 x L1.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Cylinder Crankcases Of Internal Combustion Engines (AREA)
  • Lubrication Details And Ventilation Of Internal Combustion Engines (AREA)
  • Lubrication Of Internal Combustion Engines (AREA)

Description

Die Erfindung bezieht sich auf ein Wannensystem für eine Maschinengehäusestruktur einer Brennkraftmaschine nach dem Oberbegriff des Patentanspruchs 1.The invention relates to a tray system for a machine housing structure of an internal combustion engine according to the preamble of patent claim 1.

Es ist eine Ölwanne bekannt, EP 1 264 970 B1 , die bereichsweise doppelwandig ist und eine Innenschale aus Kunststoff und einer Außenschale aus Metall aufweist. In dem durch die Innenschale und die Außenschale gebildeten Raum, strömt ein Kühlmittel für die Schmieröl aufnehmende Innenschale. Die Innenschale besitzt Abstützrippen, die an einem Boden und aufrechten Wänden der Innenschale anliegen. Und an einer Außenseite eines Bodens der Außenschale sind Kühlrippen vorgesehen. Darüber hinaus ist in die Ölwanne ein Wärmetauscher integriert, der die Wärme zwischen Kühlmittel und Umgebungsluft beeinflusst.There is an oil pan known EP 1 264 970 B1 , which is partially double-walled and has an inner shell made of plastic and an outer shell made of metal. In the space formed by the inner shell and the outer shell, a coolant for the lubricating oil receiving inner shell flows. The inner shell has Abstützrippen, which bear against a bottom and upright walls of the inner shell. And on an outer side of a bottom of the outer shell cooling fins are provided. In addition, a heat exchanger, which influences the heat between coolant and ambient air, is integrated in the oil sump.

Die FR 2 721 975 A1 gibt eine Ölwanne wieder, die an ihrer Unterseite mehrere Kühlkanäle umfasst. Die Kühlkanäle sind an den Kühlkreislauf einer Brennkraftmaschine angeschlossen, und sie werden vom Medium des Kühlkreislaufs durchströmt. In der Ölwanne und den Kühlkanälen sind Rippen vorgesehen.The FR 2 721 975 A1 is an oil pan again, which includes several cooling channels on its underside. The cooling channels are connected to the cooling circuit of an internal combustion engine, and they are flowed through by the medium of the cooling circuit. Ribs are provided in the sump and cooling channels.

Aus der DE 31 42 327 A1 geht eine BKM mit einer doppelten Wandung hervor. Ihre Wände bilden einen Hohlraum, durch den zwischen Einlass- und Auslassöffnung ein Kühlmittel strömt. Das durch den Hohlraum strömende Kühlmittel wirkt als luftschalldämmende Wandverdickung.From the DE 31 42 327 A1 A BKM comes out with a double wall. Their walls form a cavity through which a coolant flows between the inlet and outlet openings. The coolant flowing through the cavity acts as an airborne wall thickening.

In der JP S63 75550 wird eine schematische Brennkraftmaschine behandelt, die ein Zylinderkurbelgehäuse und eine Ölwanne umfasst. Die beiden letzteren sind in einer Ebene zusammengesetzt. Die Ölwanne weist eine Innenschale und eine Außenschale auf. Zwischen diesen erstreckt sich ein Kanal für den Umlauf des Kühlmittels der Brennkraftmaschine, das zur Temperaturbeeinflussung des Schmieröls in der Ölwanne dient. Zwischen Böden der Innenschale und der Außenschale ist eine Ölablassschraube vorgesehen.In the JP S63 75550 is treated a schematic internal combustion engine comprising a cylinder crankcase and an oil pan. The latter two are composed in one plane. The oil pan has an inner shell and an outer shell. Between them extends a channel for the circulation of the coolant of the internal combustion engine, which serves to influence the temperature of the lubricating oil in the oil pan. Between bottoms of the inner shell and the outer shell, an oil drain plug is provided.

Aufgabe der Erfindung ist es, ein zur Aufnahme von mittels Kühlflüssigkeit zu entwärmendem Schmieröl ausgebildetem Wannensystem für eine Brennkraftmaschine zu konzipieren, das gestaltungseinfach, funktionsoptimiert und leicht mit einem Maschinengehäuse der Brennkraftmaschine zu vereinen ist.The object of the invention is to conceive a trained for receiving by means of cooling liquid to be Entwärmendem lubricating oil pan system for an internal combustion engine, which is simple design, function optimized and easy to unite with a machine housing of the internal combustion engine.

Nach der Erfindung wird diese Aufgabe durch die Merkmale des Anspruchs 1 gelöst. Weitere, die Erfindung ausgestaltenden Merkmale sind in den Unteransprüchen enthalten.According to the invention, this object is solved by the features of claim 1. Further, the invention ausgestaltenden features are included in the subclaims.

Die mit der Erfindung hauptsächlich erzielten Vorteile sind darin zu sehen, dass die Innenwand und die Außenwand des Wannensystems sich mit definierter Konstruktionsleistung bestimmungsorientiert darstellen lassen. Dabei sind die Innenwanne und die Außenwanne aus Metall, vorzugsweise aus Leichtmetall hergestellt und weisen eine vorteilhafte Festigkeit und Wärmeleitfähigkeit auf. Und das besonders ausgeklügelte Kühlrippensystem, vor allem am Boden und den aufrechten Wänden der Innenwand, ermöglicht einen optimierten Wärmübergang zwischen vom Kühlmittel der Brennkraftmaschine beaufschlagter Innenwanne und dem Schmieröl der besagten Brennkraftmaschine. Hervorzuheben in diesem Zusammenhang ist auch das Abstützsystem zwischen den Böden der Innenwanne und der Außenwanne sowie auch der gewählte Anschluss der aufrechten Wände der zuletzt genannten Wannen an die Maschinengehäusestruktur der Brennkraftmaschine. Für entsprechende Einsatzfälle kann das Kühlrippensystem auch an der Außenseite der aufrechten Wände der Innenwanne vorgesehen sein.The advantages achieved by the invention are to be seen in the fact that the inner wall and the outer wall of the bathtub system can be represented with a defined design performance determination oriented. The inner tub and the outer tub made of metal, preferably made of light metal and have an advantageous strength and thermal conductivity. And the particularly sophisticated cooling fin system, especially on the ground and the upright walls of the inner wall, allows an optimized heat transfer between the coolant of the internal combustion engine acted upon inner trough and the lubricating oil of said internal combustion engine. Emphasizing in this context is also the support system between the bottoms of the inner tub and the outer tub as well as the selected connection of the upright walls of the latter wells to the engine housing structure of the internal combustion engine. For appropriate applications, the cooling fin system may also be provided on the outside of the upright walls of the inner tub.

Das Abstützsystem ist deshalb Beispiel gebend konstruiert, weil es eine einen Lagerbolzen besitzenden Stützzapfen am Boden der Innenwanne aufweist, der auf einer Aufnahmebuchse des Bodens der Außenwanne aufliegt, wobei der Lagerbolzen mit einer Bohrung der Aufnahmebuchse in Wirkverbindung steht. Funktionserweitert wird das Abstützsystem dadurch, dass der Lagerbolzen mit einer Ölablassschraube versehen ist. Konstruktiv geschickt gelöst ist, dass freie Enden der Innenwanne und der Außenwanne als Stützen ausgebildet sind, die mit Gegenstützen eines Verbindungsgehäuses der Maschinengehäusestruktur unter definierter Stützlast zusammenwirken. Optimiert wird letztere Lösung noch dadurch, dass die Stützen und die Gegenstützen durch eine gemeinsame Ebene zwischen der Innenwanne und der Außenwanne bzw. dem Verbindungsgehäuse begrenzt werden.The support system is exemplary constructed because it has a bearing pin owning a support pin at the bottom of the inner tub, which rests on a receiving socket of the bottom of the outer tub, wherein the bearing pin is in operative connection with a bore of the receiving socket. Functionally, the support system is extended by the fact that the bearing pin is provided with an oil drain plug. Constructively cleverly solved is that free ends of the inner tub and the outer tub are designed as supports, which interact with counter-supports of a connection housing of the machine housing structure under a defined support load. The latter solution is further optimized by the fact that the supports and the counter supports are delimited by a common plane between the inner tub and the outer tub or the connecting housing.

Das Kühlrippensystem setzt Maßstäbe in der Weise, dass es mehrere bspw. gleichmäßig verteilte Bodenkühlrippen an einer Innenseite des Bodens sowie Wandkühlrippen an einer Innenseite der aufrechten Wände der der Innenwanne umfasst, welche Bodenkühlrippen und die Wandkühlrippen im Wesentlichen senkrecht zum Boden bzw. den aufrechten Wände der Innenwand ausgerichtet sind. Dabei trägt zur besonderen Effizienz des Kühlrippensystems bei, dass sich zumindest ein der Bodenkühlrippen über eine definierte Teilhöhe einer Gesamthöhe der aufrechten Wände der Innenwanne erstreckt. Dies wird dadurch unterstützt, dass die Teilhöhe z.B. durch das Produkt 0,5 x Gesamthöhe der aufrechten Wände der Innenwanne definiert wird. Wirkungsverbessernd wirkt sich einerseits noch aus, dass zumindest ein Teil der Wandkühlrippen sich in etwa über die Teilhöhe der Bodenkühlrippen erstreckt und andererseits, dass eine erste Länge der Wandkühlrippen an der Außenseite der aufrechten Wände der Innenwanne ca. 12 bis 15 mm beträgt. Zur Effizienzoptimierung tragen auch bei, dass eine zweite Länge der Wandkühlrippen an der Außenseite der Innenwanne tragen auch bei, dass zum einen eine zweite Länge der Wandkühlrippen an der Innenseite der aufrechten Wände der Innenwanne durch den Faktor 0,8 bis 0,9 x der ersten Länge und zum anderen der Abstand zumindest zwischen einem Teil der Bodenkühlrippen und der Wandkühlrippen durch das Produkt 2 x zweite Länge der Wandkühlrippen an der Außenseite der aufrechten Wände der Innenwanne definiert wird. Schließlich ist auch noch von Vorteil, wenn die Dicke zumindest eines Teils der Boden- und Wandkühlrippen zwischen 1,5 und 2,5 mmm beträgt.The fin system sets standards such that it includes a plurality of, for example, evenly distributed floor cooling fins on an inside of the floor and wall fins on an inside of the upright walls of the inner trough, which floor cooling fins and the wall fins are substantially perpendicular to the floor or upright walls Interior wall are aligned. In this context, the particular efficiency of the cooling fin system contributes to the fact that at least one of the floor cooling fins extends over a defined partial height of an overall height of the upright walls of the inner trough. This is supported by the fact that the part height is e.g. is defined by the product 0.5 x total height of the upright walls of the inner tub. On the one hand, improving the effect still has the effect that at least part of the wall cooling ribs extends approximately above the partial height of the floor cooling ribs and, on the other hand, that a first length of the wall cooling ribs on the outside of the upright walls of the inner tub is approximately 12 to 15 mm. To optimize efficiency also contribute that a second length of the wall cooling ribs on the outside of the inner tub also contribute that on the one hand a second length of the wall cooling fins on the inside of the upright walls of the inner tub by the factor 0.8 to 0.9 x the first Length and on the other hand, the distance between at least part of the floor cooling fins and the wall cooling fins is defined by the product 2 x second length of the wall cooling fins on the outside of the upright walls of the inner tub. Finally, it is also advantageous if the thickness of at least part of the floor and wall cooling fins is between 1.5 and 2.5 mm.

In der Zeichnung ist ein Ausführungsbeispiel der Erfindung dargestellt, dass nachstehend näher erläutert wird.In the drawing, an embodiment of the invention is shown, which will be explained in more detail below.

Es zeigen

  • Fig. 1 einen Schnitt durch eine Brennkraftmaschine im Bereich eines Schmieröl aufnehmenden und Kühlwasser führenden Wannensystems,
  • Fig. 2 eine schematische Einzelheit X der Fig. 1,
  • Fig. 3 einen Schnitt nach der Linie III-III der Fig. 2.
Show it
  • Fig. 1 a section through an internal combustion engine in the region of a lubricating oil receiving and cooling water leading trough system,
  • Fig. 2 a schematic detail of the X Fig. 1 .
  • Fig. 3 a section along the line III-III of Fig. 2 ,

Eine nicht näher dargestellte Brennkraftmaschine 1 umfasst eine Maschinengehäusestruktur 2, die sich im Wesentlichen aus einem Zylinderkopf und einem Zylinderkurbelgehäuse -beide sind nicht abgebildet- zusammensetzt. In einem unteren Bereich Bu ist das das Maschinengehäusestruktur 2 mit einem Verbindungsgehäuse 3 versehen, an das ein Wannensystem 5 angeschlossen ist. Das Wannensystem 5 verfügt über eine Schmieröl der Brennkraftmaschine aufnehmende Innenwanne 6 und eine Außenwanne 7, die trogförmig ausgebildet und ineinander gesetzt sind sowie aus Metall, vorzugsweise Leichtmetall bestehen. Die Innenwanne 6 besitzt einen Boden 8 und beabstandete aufrechte Wände 9 und 10; die Außenwanne 7 einen Boden 11 und ebenfalls beabstandete aufrechte Wände 12 und 13. Die Böden 8 und 11, die Wände 9 und 10 sowie 12 und 13 verlaufen bspw. in etwa mit parallelem Abstand zueinander, so dass sich ein Zwischenraum 14 für Kühlflüssigkeit der Brennkraftmaschine 1 ergibt, mit der die Innenwanne 6 bzw. das darin enthaltene Schmieröl entwärmt wird. Dies wird durch ein Kühlrippensystem 15 unterstützt, mit dem die Innenwanne 6 das Wannensystem 5 versehen ist. Darüber hinaus ist zwischen der Innenwanne 6 und der Außenwanne 7 ein Abstützsystem 16 vorgesehen, das zur Konstanz der Abstände zwischen den Böden 8 und 11 und den aufrechten Wände 9 und 10 sowie 12 und 13 beiträgt.An internal combustion engine 1, not shown, comprises a machine housing structure 2, which are essentially composed of a cylinder head and a cylinder crankcase-both are not shown. In a lower area Bu, the machine housing structure 2 is provided with a connection housing 3, to which a tub system 5 is connected. The tub system 5 has a lubricating oil of the internal combustion engine receiving inner tub 6 and an outer tub 7, the trough-shaped and are set into each other and made of metal, preferably light metal. The inner tub 6 has a bottom 8 and spaced upright walls 9 and 10; the outer tub 7 a bottom 11 and also spaced upright walls 12 and 13. The floors 8 and 11, the walls 9 and 10 and 12 and 13 extend, for example, approximately at a parallel distance from each other, so that there is a gap 14 for the cooling liquid of the internal combustion engine 1 results, with the inner tub 6 and the lubricating oil contained therein is cooled. This is supported by a cooling fin system 15, with which the inner tub 6, the tub system 5 is provided. In addition, a support system 16 is provided between the inner tub 6 and the outer tub 7, which contributes to the constancy of the distances between the floors 8 and 11 and the upright walls 9 and 10 and 12 and 13.

Das in einer senkrechten Mittellängsebene A-A lediglich örtlich angeordnete Abstützsystem 16 umfasst einen aus einem Stück mit der Innenwanne 6 hergestellten Lagerbolzen 17. Der Lagerbolzen 17 liegt mit einem Sragen 20 auf einer Aufnahmebuchse 21 des Bodens 11 auf und ragt mit einem angeformten Führungszapfen 22 in eine Bohrung 23 der Aufnahmebuchse 21 hinein. Außerdem ist in den Führungszapfen 22 eine Ölablassschraube 24 integriert.The support system 16, which is only locally arranged in a vertical central longitudinal plane AA, comprises a bearing pin 17 made of one piece with the inner tub 6. The bearing bolt 17 rests on a receiving bushing 21 of the base 11 with a collar 20 and protrudes into a bore with an integrally formed guide pin 22 23 of the receiving socket 21 into it. In addition, an oil drain plug 24 is integrated in the guide pin 22.

Freie Enden 25, 26 und 27, 28 der Innenwand 6 und der Außenwanne 7 sind als Stützen St1, St 2 und St 3, St 4 ausgebildet, die mit Gegenstützen St5, St6 und St7, St8 des Verbindungsgehäuses 4 des Maschinengehäuses 3 mittels definierter Stützlast zusammen wirken, wobei zwischen den Stützen St1, St2 und St3 und St4 und den Gegenstützen St5, St6 und St7, St6 eine Dichtung 29 vorgesehen ist. Die Stützen St 1, St 2 und St 3, St 4 und Gegenstützen St 5, St 6 und St 7, St 8 werden durch eine bspw. horizontale Querebene Qe zwischen Innenwanne 6 und Außenwanne 7 und dem Verbindungsgehäuses 3 begrenzt. An einer Oberseite Os des Verbindungsgehäuses 3 ist eine Ölmessstabeinrichtung 30 angeordnet, wovon ein Messstab 31 einen definierten, stumpfen Winkel α zur Querebene des Wannensystems 5 einschließt. Mit einer festgelegten Messlänge MI taucht der Messstab 31 in ein Schmierölvolumen Sv der Innenwanne 6 ein, das von einem Ölspiegel Oes begrenzt wird. Damit das Schmierölvolumen Sv für den Betrieb der Brennkraftmaschine 1 funktionsgerecht gekühlt wird, ist in den Zwischenraum 14 des Wannensystems 5 ein von einer nicht gezeigten Kühlwasserpumpe der Brennkraftmaschine 1 gespeistes Kühlwasservolumen Kv eingebracht, das die Innenwanne 7 kühlend umspült.Free ends 25, 26 and 27, 28 of the inner wall 6 and the outer tub 7 are formed as supports St1, St 2 and St 3, St 4, which with counter struts St5, St6 and St7, St8 of the connection housing 4 of the machine housing 3 by means of defined Support load act together, wherein between the supports St1, St2 and St3 and St4 and the counter supports St5, St6 and St7, St6 a seal 29 is provided. The supports St 1, St 2 and St 3, St 4 and counter supports St 5, St 6 and St 7, St 8 are limited by an example. Horizontal transverse plane Qe between the inner tub 6 and outer tub 7 and the connecting housing 3. On an upper side Os of the connection housing 3, an oil dipstick device 30 is arranged, of which a dipstick 31 encloses a defined, obtuse angle α to the transverse plane of the bath system 5. With a predetermined measuring length MI, the dipstick 31 dips into a lubricating oil volume Sv of the inner tub 6, which is delimited by an oil level Oes. So that the lubricating oil volume Sv is functionally cooled for the operation of the internal combustion engine 1, a cooling water volume Kv fed by a cooling water pump, not shown, of the internal combustion engine 1 is introduced into the intermediate space 14 of the bathtub system 5, which circulates the inner tub 7 in a cooling manner.

Das Kühlrippensystem 15 weist an einer Innenseite 32 des Bodens 8 der Innenwanne 6 mehrere z.B. gleichmäßig verteilte Bodenkühlrippen 33 auf. Ebenfalls an der Innenseite 32 der Innenwanne 6, und zwar an den aufrechten Wänden 9 und 10 sind Wandkühlrippen 34 und 35 angeformt. Ihre Anordnung entspricht im Wesentlichen der der Bodenkühlrippen 33. Und sowohl die Bodenkühlrippen 33 wie auch die Wandkühlrippen 34 und 35 sind senkrecht zum Boden 8 bzw. den aufrechten Wänden 6 und 7 der Innenwanne 6 ausgerichtet, wobei die mittlere Dicke 36 der zuletzt genannten Rippen über ihre Länge betrachtet ca. 1,5 bis 2,5 mm misst.The cooling fin system 15 has on an inner side 32 of the bottom 8 of the inner tub 6 a plurality of e.g. evenly distributed floor cooling ribs 33 on. Also on the inside 32 of the inner tub 6, namely on the upright walls 9 and 10 wall cooling fins 34 and 35 are formed. Their arrangement corresponds essentially to that of the floor cooling fins 33. And both the floor cooling fins 33 and the wall cooling fins 34 and 35 are perpendicular to the bottom 8 and the upright walls 6 and 7 of the inner trough 6 aligned, the average thickness 36 of the latter ribs on their length measures about 1.5 to 2.5 mm.

Zumindest ein Teil der Bodenrippen 33 erstreckt sich über eine definierte Teilhöhe Th einer Gesamthöhe Hges der aufrechten Wände 9 und 10 der Innenwanne 6 bzw. des Wannensystems 5. Die Teilhöhe Th der Bodenkühlrippen 33 erstreckt sich im Ausführungsbeispiel bis in die Nähe des Ölspiegels Oes des Schmierölvolumens Sv und sie lässt sich durch das Produkt 0,5 x Gesamthöhe Hges definieren. Darüber hinaus erstreckt sich zumindest ein Teil der Wandkühlrippen 34 und 35 in Richtung Querebene Qe z.B. in etwa über die Teilhöhe Th der Bodenkühlrippen 33.At least a part of the bottom ribs 33 extends over a defined partial height Th of a total height Hges of the upright walls 9 and 10 of the inner tub 6 and of the tub system 5. The partial height Th of the bottom cooling ribs 33 extends in the exemplary embodiment to near the oil level Oes of the lubricating oil volume Sv and she can be defined by the product 0.5 x total height Hges. In addition, at least a portion of the wall cooling fins 34 and 35 extends in the direction of the transverse plane Qe, for example, approximately over the partial height Th of the floor cooling fins 33.

Das Kühlrippensystem 15 umfasst an einer Außenseite 37 der aufrechten Wände 9 und 10 der Innenwanne 6 durch Wandkühlrippen 38 und 39. Eine erste Länge L1 der Wandkühlrippen 38 und 39 an der Außenseite beträgt ca. 12 bis 15 mm; eine zweite Länge L2 der Wandkühlrippen 34 und 35 an der Innenseite 32 der Innenwanne 6 wird durch einen Faktor 0,8 bis 0,9 x L1 gebildet. Schließlich wird der Abstand As zwischen zumindest einem Teil der Wandkühlrippen 34 und 35 bzw. 38 und 39 sowie den Bodenkühlrippen 33 durch das Produkt 2 x L1 definiert.The fin system 15 comprises on an outer side 37 of the upright walls 9 and 10 of the inner tub 6 by wall cooling ribs 38 and 39. A first length L1 of the wall cooling ribs 38 and 39 on the outside is about 12 to 15 mm; a second length L2 of the wall cooling fins 34 and 35 on the inside 32 of the inner tub 6 is formed by a factor of 0.8 to 0.9 x L1. Finally, the distance As between at least part of the wall cooling fins 34 and 35 or 38 and 39 and the bottom cooling fins 33 is defined by the product 2 x L1.

Claims (13)

  1. Pan system for a machine housing structure of an internal combustion engine, which has two inner and outer pans which are nested in one another, are trough-shaped in cross section and have bottoms and upright walls, from which the inner pan receives lubricating oil from the internal combustion engine, and the outer pan, together with the bottom and the upright walls, extends at least in regions at a distance from the bottom and the walls of the inner pan, such that a channel-like intermediate space is formed which contains the cooling liquid of the internal combustion engine for influencing the temperature of the inner pan, ribs being provided on the inner walls and the outer walls, and the inner pan and the outer pan interacting by means of a support system, characterized in that the inner pan (6) and the outer pan (7) consist of metal material and the inner pan (6) is provided with a cooling rib system (15) on an inner side (32) of the bottom (8) and on the upright walls (6 and 7) for optimizing heat transfer and in that the cooling rib system (15) is provided on the outer side (37) of the upright walls (9 and 10) of the inner pan (6) and has wall cooling ribs (38 and 39), the support system (16) being active between the bottoms (8 and 11) of the inner pan (6) and the outer pan (7) and in that the upright walls (9, 10 and 12 and 13) of the inner pan (6) and the outer pan (7) are connected to the machine housing structure (2), which support system (16) has a bearing pin (17) on the bottom (8) of the inner pan (6), which bearing pin (17), together with a support collar (20), rests on a receiving bush (21) of the bottom (11) of the outer pan (7), the bearing pin (17), together with a guiding pin (22), protruding into a bore (23) in the receiving bush (21).
  2. Pan system according to claim 1, characterized in that the bearing pin (17) is provided with an oil drain plug (24).
  3. Pan system according to claim 1, characterized in that free ends (25, 26, 27 and 28) of the upright walls (9, 10 and 12, 13) of the inner pan (6) and the outer pan (7) are designed as supports (St1, St2, St3 and St4) which interact with counter supports (St5, St6, St7 and St8) of a connecting housing (3) of the machine housing structure (2) under a defined support load.
  4. Pan system according to claim 3, characterized in that the supports (St1, St2, St3 and St4) and the counter supports (St5, St6 St7 and St8) are delimited by a common transverse plane (Qe) between the inner pan (6) and the outer pan (7) or the connecting housing (3).
  5. Pan system according to claim 1, characterized in that the cooling rib system (15) has a plurality of, for example, uniformly distributed bottom cooling ribs (33) on an inner side (32) of the bottom (8) and wall cooling ribs (34 and 35) on the inner side (32) of the upright walls (9 and 10) of the inner pan (6).
  6. Pan system according to claim 5, characterized in that the bottom cooling ribs (33) and the wall cooling ribs (34 and 35) are oriented substantially perpendicularly to the bottom (8) and to the upright walls (9 and 10) of the inner pan (6), respectively.
  7. Pan system according to claims 5 and 6, characterized in that at least some of the bottom cooling ribs (33) extend over a defined first partial height (Th) of a total height (Hges) of the upright walls (9 and 10) of the inner pan (6).
  8. Pan system according to claim 7, characterized in that the partial height (Th) of the bottom cooling ribs (33) is defined, for example, by the product 0.5 x total height (Hges) of the upright walls (9 and 10) of the inner pan (6).
  9. Pan system according to one or more of the preceding claims, characterized in that at least some of the wall cooling ribs (34 and 35) extend approximately over the partial height (Th) of the bottom cooling ribs (33).
  10. Pan system according to claim 9, characterized in that a first length (L1) of the wall cooling ribs (38 and 39) on an outer side (37) of the upright walls (12 and 13) of the inner pan (6) is approximately 12 to 15 mm.
  11. Pan system according to claim 9, characterized in that a second length (L2) of the wall cooling ribs (34 and 35) on the inner side (32) of the upright walls (9 and 10) of the inner pan is defined by a factor of 0.8 to 0.9 x the first length (L1) of the wall cooling ribs (38 and 39) on the outer side (37) of the inner pan (6).
  12. Pan system according to one or more of the preceding claims, characterized in that the distance (As) at least between some of the bottom cooling ribs (33) and the wall cooling ribs (34 and 35) is approximately defined by the product 2 x the first length (L1) of the wall cooling ribs (38 and 39) on the outer side (37) of the upright walls (9 and 1).
  13. Pan system according to one or more of the preceding claims, characterized in that a thickness (36) of at least some of the bottom cooling ribs (33) and the wall cooling ribs (34 and 35 or 38 and 39) is between 1.5 and 2.5 mm.
EP16000593.0A 2015-03-14 2016-03-11 Shell system for a machine housing structure for a combustion engine Active EP3070280B1 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102015003282.8A DE102015003282B4 (en) 2015-03-14 2015-03-14 Tub system for a machine housing structure of an internal combustion engine

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EP3070280A1 EP3070280A1 (en) 2016-09-21
EP3070280B1 true EP3070280B1 (en) 2019-08-28

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US (1) US10221731B2 (en)
EP (1) EP3070280B1 (en)
JP (1) JP2016169737A (en)
DE (1) DE102015003282B4 (en)
ES (1) ES2754390T3 (en)

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DE102015003282B4 (en) 2017-06-29
EP3070280A1 (en) 2016-09-21
US20160265402A1 (en) 2016-09-15
ES2754390T3 (en) 2020-04-17
DE102015003282A1 (en) 2016-09-15
US10221731B2 (en) 2019-03-05
JP2016169737A (en) 2016-09-23

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