EP1555405B1 - Internal combustion engine - Google Patents

Internal combustion engine Download PDF

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Publication number
EP1555405B1
EP1555405B1 EP04028081A EP04028081A EP1555405B1 EP 1555405 B1 EP1555405 B1 EP 1555405B1 EP 04028081 A EP04028081 A EP 04028081A EP 04028081 A EP04028081 A EP 04028081A EP 1555405 B1 EP1555405 B1 EP 1555405B1
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EP
European Patent Office
Prior art keywords
internal combustion
combustion engine
bearing
housing
crankshaft
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EP04028081A
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German (de)
French (fr)
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EP1555405A1 (en
Inventor
Eva Jerger
Markus Kielsmeier
Manfred Kloft
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Volkswagen AG
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Volkswagen AG
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Publication of EP1555405A1 publication Critical patent/EP1555405A1/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B77/00—Component parts, details or accessories, not otherwise provided for
    • F02B77/11—Thermal or acoustic insulation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B75/00—Other engines
    • F02B75/06—Engines with means for equalising torque
    • 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
    • F01M1/02—Pressure lubrication using lubricating pumps
    • F01M2001/0253—Pressure lubrication using lubricating pumps characterised by the pump driving means
    • F01M2001/0276—Pressure lubrication using lubricating pumps characterised by the pump driving means driven by a balancer shaft

Definitions

  • the invention relates to an internal combustion engine having a device for compensating for mass effects, which has a balancing shaft housing supporting at least one balancing shaft which can be driven by a crankshaft.
  • Such an internal combustion engine is off US 55 35 643 A known.
  • the internal combustion engine disclosed therein has a mass action compensating device having a housing disposed below a crankcase and within an oil pan and secured to the crankcase at the location of crank bearings. In the housing two drivable by the crankshaft balance shafts are housed.
  • a torque compensation device for an internal combustion engine with a housing which is screwed to the crankcase and having a bore for a balance shaft.
  • an oil pump is provided to supply the internal combustion engine with oil.
  • the housing has a cavity in which the oil pump is housed.
  • An engine balance unit which is intended for an engine with a cylinder block and a crankshaft, with an attached to an underside of the cylinder block sump shows DE 198 51 547 A1 ; wherein in the oil pan, a housing is used to support Aüs Diseaseswellen with balancing weights.
  • On one side of the oil pan teine oil pump is provided with a sprocket having a pump shaft.
  • the crankshaft rotates.
  • the rotation of the crankshaft is transmitted to the sprocket by means of a chain to turn and operate the oil pump.
  • the rotation of the oil pump is further transmitted via a clutch to a first of the balance shafts, which sets a second balance shaft via gears in rotation.
  • the invention has for its object to provide an internal combustion engine of the type mentioned with increased rigidity and reduced noise, which has an increased ease of installation.
  • the balance shaft housing as a bearing bridge for connecting crankshaft bearing caps, the number of components and thus the number of connection points between the individual components of the internal combustion engine is reduced, which has an immediate increase in stiffness result.
  • the rigidity of the internal combustion engine can be significantly increased overall.
  • the vibrations generated by the internal combustion engine itself during operation and thus also the noise are significantly reduced.
  • a mechanical and, on the other hand, an acoustic signal is used with the invention effective stiffening of the internal combustion engine, with the result that the durability increases and the noise level decreases.
  • the unit of balance shaft housing and bearing bridge can be prefabricated modular.
  • the component integration according to the invention also advantageously leads to a weight saving, which helps to reduce the consumption of fuel, especially in internal combustion engines in motor vehicles.
  • the balance shaft housing has a connection to the bearing caps exhibiting, the bearing bridge forming housing lower part and a housing cover designed as a housing upper part.
  • the lower housing part serve both as a storage shell for the balance shaft and as a stabilizing bearing bridge.
  • the bearing bridge connects some selected bearing caps of crankshaft bearings.
  • the bearing bridge bearing cap of all crankshaft bearings with each other and connects to a crankcase. In this way, a particularly high strength and torsional stiffness of the internal combustion engine is achieved by connecting the bearing cap directly to the regularly very stiff crankcase.
  • the bearing bridge is connected to side walls of the crankcase. This connection can preferably take place by means of a screw connection of the bearing bridge to the crankcase.
  • the bearing bridge has lateral connection tabs which are bolted to the side walls of the crankcase.
  • connection straps are flexible in bending in a direction parallel to the axis of a cylinder of the internal combustion engine and rigid in a direction parallel to the crankshaft longitudinal axis. Due to the flexurally soft design of the connection straps in the direction parallel to the cylinder axis, both manufacturing tolerances can be compensated particularly well and different thermal expansions can be accommodated. At the same time, the bending-resistant formation of the connecting straps in the direction parallel to the crankshaft longitudinal axis prevents bearing cover vibrations.
  • the second balance shaft can then be driven by the first balance shaft.
  • One of the two balance shafts preferably drives an oil pump arranged on the balance shaft housing, in particular the second balance shaft.
  • the oil pump in the power flow is the last component and prevents coupled via a gear transmission balancer shafts as a load rattle the gears.
  • balance shafts for example, by means of a chain or toothed belt drive or via a spur gear transmission with each other.
  • the balance shafts are connected to each other via a helical gear transmission.
  • the oil pump is preceded by a gear that translates a speed of the oil pump driving balancing shaft in the slow.
  • a gear that translates a speed of the oil pump driving balancing shaft in the slow.
  • crankcase consisting essentially of an aluminum alloy, according to another advantageous development of the invention.
  • the term essentially means that some, a lower volume fraction constituents such as bearing bushes of the crankcase can be made of a different material.
  • FIG. 1 shows a section of an internal combustion engine 1 with a device 2 for the compensation of mass effects, which is driven by a crankshaft of the internal combustion engine 1, not shown here.
  • the device 2 for compensating for mass effects comprises a balance shaft housing with a lower housing part designed as a bearing bridge 4 and an upper housing part designed as a housing cover 6.
  • the internal combustion engine is a 4-cylinder in-line engine of a passenger car.
  • the bearing bridge 4 connects bearing cap 8 of crankshaft bearings of the crankshaft, not shown here, and is fastened with the bearing caps 8 to a crankcase 10 of the internal combustion engine 1 by means of bearing cap screws 12 and hexagon screws 14.
  • two balance shafts 16, 18 are mounted, which are driven by a mounted on the crankshaft sprocket 20, a chain 22 and a mounted on the first balance shaft 16 second sprocket 24.
  • the balance shafts 16, 18 with balancing weights are located with their centers of gravity in the middle of the engine 1 and at the same distance from the center of the crankshaft.
  • the housing cover 6 is fastened with collar bolts 26 on the bearing bracket 4. The exact position of the housing cover 6 to the bearing bracket 4 forming housing lower part is ensured by means of dowel sleeves 28.
  • the first balance shaft 16 is radially mounted at four bearing points 30, 32, 34, 36, the second balance shaft 18 at three bearings 38, 40, 42.
  • the bearings of the balance shafts 16, 18 consist of plain bearings, wherein the balance shafts 16, 18 due to from them attainable high speeds (up to 13,600 1 / min) in bearing shells 44 and bearing bushes 46, 48 are embedded.
  • the plain bearings are supplied with oil from the crankcase 10 via channels, not shown here. These channels extend both in the bearing bridge 4 and in the housing cover. 6
  • a mounted on the first balancer shaft 16 first helical gear 50 forms together with a mounted on the second balance shaft 18 second helical gear 52, a first gear stage through which the second balance shaft 18 is driven with one of the first balance shaft 16 corresponding speed.
  • the thrust bearings are located on the two sides of the helical gears 50, 52, the respective mating surfaces are located on the bearing bridge 4 and the housing cover 6.
  • the axial bearing is a lateral slipping (back and sideslip) and rattling of the balance shafts 16, 18th prevented in the balance shaft housing.
  • the device 2 for compensating for mass effects further comprises an oil pump 54 of the internal combustion engine 1.
  • the oil pump 54 is an adjustable external gear pump, which is screwed into the housing cover 6 of the balance shaft housing by means of collar bolts 56.
  • the drive of the oil pump 54 is effected by the second balance shaft 18.
  • a drive gear 58 is arranged with a comparatively small diameter on the second balance shaft 18, in which a arranged on an oil pump shaft 60, a larger diameter having input gear 62 engages.
  • the oil pump shaft 60 and first and second balance shaft 16, 18 are arranged parallel to each other.
  • the drive gear 58 and input gear 62 are associated with a second gear stage driving the oil pump 54.
  • the speed of the oil pump shaft 60 thus corresponds to half the speed of the two balancer shafts 16, 18.
  • the oil pump 54 is the last component in the power flow through the balance shafts 16, 18. Since the balance shafts 16, 18 are alternately accelerated and decelerated during each revolution of the crankshaft, there is basically a constant change in the teeth of the gears 50th , 52 of the first gear stage with the consequence of unwanted noise. Due to the braking torque caused by the oil pump 54, this basic system change is prevented in the arrangement chosen here, the teeth of the gears 50, 52 are always in the same system, whereby the noise is minimized. The same applies to the second gear stage with the drive gear 58 on the second balance shaft 18 and the input gear 62 on the oil pump shaft 60th
  • FIG. 2 a partial view of the internal combustion engine 1 is shown in assembled construction.
  • the balance shaft housing 64 is closed here, the housing cover 6 is screwed with the collar bolts 26 on the bearing bracket 4, which in turn is screwed to the hexagonal screws 14 on side walls 66, 68 of the crankcase 10.
  • the bearing bridge 4 has lateral connecting straps 70, through which the hexagon screws 14 extend.
  • connection straps 70 are exemplified in a direction parallel to the axis of a cylinder of the internal combustion engine 1 by a straight line 72, bendable and in a direction parallel to the crankshaft longitudinal axis, exemplified by a straight line 74, rigid.

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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)
  • Acoustics & Sound (AREA)
  • Lubrication Of Internal Combustion Engines (AREA)
  • Cylinder Crankcases Of Internal Combustion Engines (AREA)
  • Valve Device For Special Equipments (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)

Abstract

The engine has housing for a crankshaft which is balanced and has an oil pump. The housing has a plate (8) connected to crankshaft bearings. The housing connects to the plate having a screen end with a housing lower and upper part designed forming a frame cover (6). A bridge connects the plate to crankshaft bearings and to a crank case (10).

Description

Die Erfindung betrifft eine Brennkraftmaschine mit einer Vorrichtung zum Ausgleich von Massenwirkungen, die ein zumindest eine von einer Kurbelwelle antreibbare Ausgleichswelle lagerndes Ausgleichswellengehäuse aufweist.The invention relates to an internal combustion engine having a device for compensating for mass effects, which has a balancing shaft housing supporting at least one balancing shaft which can be driven by a crankshaft.

Eine derartige Brennkraftmaschine ist aus US 55 35 643 A bekannt. Die dort offenbarte Brennkraftmaschine weist eine Vorrichtung zum Ausgleich von Massenwirkungen auf, die ein Gehäuse besitzt, das unterhalb eines Kurbelgehäuses und innerhalb einer Ölwanne angeordnet sowie am Kurbelgehäuse befestigt ist, und zwar am Ort von Kurbellagern. In dem Gehäuse sind zwei von der Kurbelwelle antreibbare Ausgleichswellen untergebracht.Such an internal combustion engine is off US 55 35 643 A known. The internal combustion engine disclosed therein has a mass action compensating device having a housing disposed below a crankcase and within an oil pan and secured to the crankcase at the location of crank bearings. In the housing two drivable by the crankshaft balance shafts are housed.

Des Weiteren offenbart DE 100 07 660 A1 eine Vorrichtung zum Momentenausgleich für eine Brennkraftmaschine mit einem Gehäuse, das an das Kurbelgehäuse angeschraubt ist und das eine Bohrung für eine Ausgleichswelle aufweist. Zur Versorgung der Brennkraftmaschine mit Öl ist eine Ölpumpe vorgesehen. Das Gehäuse weist einen Hohlraum auf, in dem die Ölpumpe untergebracht ist.Further disclosed DE 100 07 660 A1 a torque compensation device for an internal combustion engine with a housing which is screwed to the crankcase and having a bore for a balance shaft. To supply the internal combustion engine with oil, an oil pump is provided. The housing has a cavity in which the oil pump is housed.

Über Montage und Befestigung von Lagerdeckeln der Kurbelwellenlager sagt dieser Stand der Technik nichts aus.About mounting and mounting bearing caps of the crankshaft bearing says this prior art nothing.

Eine Motorausgleichseinheit, die für einen Motor mit einem Zylinderblock und einer Kurbelwelle bestimmt ist, mit einer an einer Unterseite des Zylinderblocks angebrachtes Ölwanne zeigt DE 198 51 547 A1 ; wobei in die Ölwanne ein Gehäuse zum Stützen von Aüsgleichswellen mit Ausgleichsgewichten eingesetzt ist. An einer Seite der Ölwanne ist teine Ölpumpe mit einer ein Kettenrad aufweisenden Pumpenwelle vorgesehen. Während des Betriebs des Motors dreht sich die Kurbelwelle. Die Drehung der Kurbelwelle wird mittels einer Kette auf das Kettenrad übertragen, um die Ölpumpe zu drehen und zu betreiben. Die Drehung der Ölpumpe wird des Weiteren über eine Kupplung auf eine erste der Ausgleichswellen übertragen, welche über Zahnräder eine zweite Ausgleichswelle in Drehung versetzt.An engine balance unit, which is intended for an engine with a cylinder block and a crankshaft, with an attached to an underside of the cylinder block sump shows DE 198 51 547 A1 ; wherein in the oil pan, a housing is used to support Aüsgleichswellen with balancing weights. On one side of the oil pan teine oil pump is provided with a sprocket having a pump shaft. During operation of the engine, the crankshaft rotates. The rotation of the crankshaft is transmitted to the sprocket by means of a chain to turn and operate the oil pump. The rotation of the oil pump is further transmitted via a clutch to a first of the balance shafts, which sets a second balance shaft via gears in rotation.

Außerdem offenbart DE 197 49 300 A1 eine baulich und antriebsmäßig mit einer Ölpumpe kombinierte Brennkraftmaschine mit einer Ausgleichswellen aufweisenden Massenausgleichsvorrichtung II. Ordnung. Dabei ist die Ölpumpe bezüglich der Ausgleichswellen mit einer geringeren Drehzahl antreibbar. Die Ölpumpe steht mittels eines drehzahlsteigernden Getriebes mit einer der Ausgleichswellen in Antriebsverbindung, und die Ausgleichswellen sind über ein Zahnradpaar miteinander drehverbunden.Also revealed DE 197 49 300 A1 a structurally and drivingly combined with an oil pump internal combustion engine having a balance shafts mass balance device II. order. In this case, the oil pump with respect to the balance shafts with a lower speed can be driven. The oil pump is by means of a speed-increasing gear with one of the balance shafts in drive connection, and the balance shafts are rotatably connected to each other via a gear pair.

Ferner ist aus DE 38 24 553 C1 eine spezielle Kurbelwellenlagerung für eine Brennkraftmaschine mit einer Kurbelwelle und mit über eine Lagerbrücke verbundenen Hauptlagerstühlen bekannt, wobei die Lagerbrücke zwischen den Hauptlagerstühlen mit von der Kurbelwellenlängsachse abweichendem Verlauf sich erstreckenden Versteifungsrippen versehen ist.Furthermore, it is off DE 38 24 553 C1 a special crankshaft bearing for an internal combustion engine with a crankshaft and connected via a bearing bridge main storage chairs known, the bearing bridge is provided between the main storage chairs with deviating from the crankshaft longitudinal course extending stiffening ribs.

Der Erfindung liegt die Aufgabe zugrunde, eine Brennkraftmaschine der eingangs genannten Art mit einer erhöhten Steifigkeit und verminderter Geräuschentwicklung zu liefern, die eine erhöhte Montagefreundlichkeit aufweist.The invention has for its object to provide an internal combustion engine of the type mentioned with increased rigidity and reduced noise, which has an increased ease of installation.

Diese Aufgabe wird gelöst mit einer Brennkraftmaschine der eingangs genannten Art, bei der zumindest ein Teil des Ausgleichswellengehäuses als Lagerdeckel der Kurbelwellenlager untereinander und mit dem Kurbelgehäuse verbindende Lagerbrücke ausgebildet sowie zusammen mit den Lagerdeckeln am Kurbelgehäuse befestigt ist. Die Unteransprüche betreffen besonders zweckmäßige Weiterbildungen der Erfindung.This object is achieved with an internal combustion engine of the type mentioned, in which at least a part of the balance shaft housing is formed as a bearing cap of the crankshaft bearing with each other and with the crankcase connecting bearing bridge and secured together with the bearing caps on the crankcase. The subclaims relate to particularly expedient developments of the invention.

Durch die erfindungsgemäße Ausbildung des Ausgleichswellengehäuses als Lagerbrücke zur Verbindung von Kurbelwellenlagerdeckeln wird die Bauteilanzahl und damit auch die Anzahl der Verbindungsstellen zwischen den einzelnen Bauteilen der Brennkraftmaschine reduziert, was unmittelbar eine Erhöhung der Steifigkeit zur Folge hat. Es erfolgt zudem eine Versteifung sowohl von Lagerstühlen der Kurbelwellenlager an sich als auch eines Kurbelgehäuses der Brennkraftmaschine. Auf diese Weise kann die Steifigkeit der Brennkraftmaschine insgesamt erheblich erhöht werden. Gleichzeitig werden die von der Brennkraftmaschine selbst bei ihrem Betrieb erzeugten Schwingungen und damit auch die Geräuschentwicklung nennenswert vermindert. Mit der Erfindung erfolgt somit einerseits eine mechanische und andererseits eine akustisch wirksame Versteifung der Brennkraftmaschine mit der Folge, dass die Dauerhaltbarkeit steigt und das Geräuschniveau sinkt. Da die geringere Bauteilanzahl sowohl Logistik und Lagerhaltung als auch Zusammenbau der erfindungsgemäßen Brennkraftmaschine vereinfacht, kann diese zudem besonders kostengünstig hergestellt werden. Weiterhin von Vorteil ist dabei, dass sich die Einheit aus Ausgleichswellengehäuse und Lagerbrücke modulartig vorfertigen lässt. Die erfindungsgemäße Bauteilintegration führt außerdem vorteilhaft zu einer Gewichtseinsparung, die insbesondere bei Brennkraftmaschinen in Kraftfahrzeugen den Verbrauch an Treibstoff zu verringern hilft.Due to the inventive design of the balance shaft housing as a bearing bridge for connecting crankshaft bearing caps, the number of components and thus the number of connection points between the individual components of the internal combustion engine is reduced, which has an immediate increase in stiffness result. There is also a stiffening both of bearing blocks of the crankshaft bearings per se and a crankcase of the internal combustion engine. In this way, the rigidity of the internal combustion engine can be significantly increased overall. At the same time the vibrations generated by the internal combustion engine itself during operation and thus also the noise are significantly reduced. Thus, on the one hand, a mechanical and, on the other hand, an acoustic signal is used with the invention effective stiffening of the internal combustion engine, with the result that the durability increases and the noise level decreases. Since the smaller number of components simplifies both logistics and warehousing and assembly of the internal combustion engine according to the invention, this can also be made particularly cost. Another advantage is that the unit of balance shaft housing and bearing bridge can be prefabricated modular. The component integration according to the invention also advantageously leads to a weight saving, which helps to reduce the consumption of fuel, especially in internal combustion engines in motor vehicles.

Gemäß einer vorteilhaften Weiterbildung der Erfindung besitzt das Ausgleichswellengehäuse ein Verbindungen zu den Lagerdeckeln aufweisendes, die Lagerbrücke bildendes Gehäuseunterteil und ein als Gehäusedeckel ausgebildetes Gehäuseoberteil. Auf diese Weise kann die funktionale Integration der Bauteile erhöhend und den Zusammenbau vereinfachend das Gehäuseunterteil sowohl als Lagerungsschale für die Ausgleichswelle als auch als stabilisierende Lagerbrücke dienen.According to an advantageous embodiment of the invention, the balance shaft housing has a connection to the bearing caps exhibiting, the bearing bridge forming housing lower part and a housing cover designed as a housing upper part. In this way, the functional integration of the components increasing and simplifying the assembly, the lower housing part serve both as a storage shell for the balance shaft and as a stabilizing bearing bridge.

Man könnte sich vorstellen, dass die Lagerbrücke einige ausgewählte Lagerdeckel von Kurbelwellenlagern verbindet. Besonders vorteilhaft ist es hingegen, wenn gemäß einer anderen Weiterbildung der Erfindung die Lagerbrücke Lagerdeckel aller Kurbelwellenlager untereinander und mit einem Kurbelgehäuse verbindet. Auf diese Weise wird durch die Anbindung der Lagerdeckel unmittelbar an das regelmäßig sehr steife Kurbelgehäuse eine besonders hohe Festigkeit und Verwindungssteifigkeit der Brennkraftmaschine erreicht.One could imagine that the bearing bridge connects some selected bearing caps of crankshaft bearings. In contrast, it is particularly advantageous if, according to another embodiment of the invention, the bearing bridge bearing cap of all crankshaft bearings with each other and connects to a crankcase. In this way, a particularly high strength and torsional stiffness of the internal combustion engine is achieved by connecting the bearing cap directly to the regularly very stiff crankcase.

Vorteilhaft werden insbesondere Längsschwingungen der Lagerbrücke weitestgehend verhindert, wenn gemäß einer anderen Weiterbildung der Erfindung die Lagerbrücke an Seitenwände des Kurbelgehäuses angebunden ist. Diese Anbindung kann vorzugsweise mittels einer Verschraubung der Lagerbrücke an dem Kurbelgehäuse erfolgen.In particular, longitudinal vibrations of the bearing bracket are advantageously prevented as far as possible, according to another embodiment of the invention, the bearing bridge is connected to side walls of the crankcase. This connection can preferably take place by means of a screw connection of the bearing bridge to the crankcase.

Dabei ist es für eine Montage und (zum Beispiel im Wartungsfall) für eine Demontage der Brennkraftmaschine von besonderem Vorteil, wenn gemäß einer zusätzlichen Weiterbildung der Erfindung die Lagerbrücke seitliche Anbindungslaschen aufweist, die mit den Seitenwänden des Kurbelgehäuses verschraubt sind.It is for a mounting and (for example, in case of maintenance) for disassembly of the internal combustion engine of particular advantage, when according to an additional embodiment of the invention, the bearing bridge has lateral connection tabs which are bolted to the side walls of the crankcase.

Gemäß einer vorteilhaften Weiterbildung der Erfindung sind die Anbindungslaschen in einer zur Achse eines Zylinders der Brennkraftmaschine parallelen Richtung biegeweich und in einer zur Kurbelwellenlängsachse parallelen Richtung biegesteif. Durch die biegeweiche Ausbildung der Anbindungslaschen in der zur Zylinderachse parallelen Richtung können besonders gut sowohl Fertigungstoleranzen ausgeglichen als auch unterschiedliche Wärmedehnungen aufgenommen werden. Gleichzeitig verhindert die biegesteife Ausbildung der Anbindungslaschen in der zur Kurbelwellenlängsachse parallelen Richtung Lagerdeckelschwingungen.According to an advantageous development of the invention, the connection straps are flexible in bending in a direction parallel to the axis of a cylinder of the internal combustion engine and rigid in a direction parallel to the crankshaft longitudinal axis. Due to the flexurally soft design of the connection straps in the direction parallel to the cylinder axis, both manufacturing tolerances can be compensated particularly well and different thermal expansions can be accommodated. At the same time, the bending-resistant formation of the connecting straps in the direction parallel to the crankshaft longitudinal axis prevents bearing cover vibrations.

Von besonderem Vorteil zum Ausgleich von Massenkräften II. Ordnung, insbesondere bei 4-Zylinder-Brennkraftmaschinen, ist es, wenn die Brennkraftmaschine zwei Ausgleichswellen aufweist. Gemäß einer vorteilhaften Weiterbildung der Erfindung ist dann die zweite Ausgleichswelle von der ersten Ausgleichswelle antreibbar. Vorzugsweise treibt eine der beiden Ausgleichswellen eine an dem Ausgleichswellengehäuse angeordnete Ölpumpe an, insbesondere die zweite Ausgleichswelle. Auf diese Weise ist die Ölpumpe im Kraftfluss das letzte Bauelement und verhindert bei über ein Zahnradgetriebe gekoppelten Ausgleichswellen als Lastabnehmer ein Klappern der Zahnräder. Durch diese Maßnahme erfolgt eine weitere nennenswerte Absenkung des Geräuschniveaus der Brennkraftmaschine, eine weitere Reduktion der Bauteilanzahl und eine weitere Funktionsintegration bezüglich eines vormontierbaren Moduls aus Ausgleichswellengehäuse, Lagerbrücke und Ölpumpe.Of particular advantage for the compensation of inertial forces II. Order, in particular in 4-cylinder internal combustion engines, it is when the internal combustion engine has two balance shafts. According to an advantageous development of the invention, the second balance shaft can then be driven by the first balance shaft. One of the two balance shafts preferably drives an oil pump arranged on the balance shaft housing, in particular the second balance shaft. In this way, the oil pump in the power flow is the last component and prevents coupled via a gear transmission balancer shafts as a load rattle the gears. By this measure, a further significant reduction of the noise level of the internal combustion engine, a further reduction of the number of components and a further functional integration with respect to a preassemblable module of balance shaft housing, bearing bracket and oil pump.

Man könnte sich vorstellen, die Ausgleichswellen beispielsweise mittels eines Ketten- oder Zahnriementriebs oder über ein geradverzahntes Zahnradgetriebe miteinander zu koppeln. Für einen möglichst geräuscharmen Lauf und eine hohe Dauerhaltbarkeit ist es jedoch von Vorteil, wenn gemäß einer anderen Weiterbildung der Erfindung die Ausgleichswellen über ein schrägverzahntes Zahnradgetriebe miteinander verbunden sind.One could imagine to couple the balance shafts, for example, by means of a chain or toothed belt drive or via a spur gear transmission with each other. For quietest possible running and high durability, it is advantageous if, according to another embodiment of the invention, the balance shafts are connected to each other via a helical gear transmission.

Gemäß einer anderen vorteilhaften Weiterbildung der Erfindung ist der Ölpumpe ein Getriebe vorgeschaltet, das eine Drehzahl der die Ölpumpe antreibenden Ausgleichswelle ins Langsame übersetzt. Durch eine solche Übersetzung ins Langsame, umgangssprachlich auch als Untersetzung bezeichnet, wird der Wirkungsgrad der Ölpumpe erhöht.According to another advantageous embodiment of the invention, the oil pump is preceded by a gear that translates a speed of the oil pump driving balancing shaft in the slow. Through such a translation into the slow, colloquially referred to as reduction, the efficiency of the oil pump is increased.

Eine Brennkraftmaschine mit besonders geringem Gewicht, die insbesondere bei Verwendung in einem Kraftfahrzeug zu einem reduzierten Kraftstoffverbrauch führt, wird dadurch erhalten, dass gemäß einer anderen vorteilhaften Weiterbildung der Erfindung das Kurbelgehäuse im Wesentlichen aus einer Aluminiumlegierung besteht; der Begriff im Wesentlichen bedeutet dabei, dass einige, einen geringeren Volumenanteil ausmachende Bestandteile wie zum Beispiel Lagerbuchsen des Kurbelgehäuses aus einem anderen Werkstoff bestehen können. Bei einer Brennkraftmaschine mit einem Kurbelgehäuse aus einer Aluminiumlegierung treten zudem die oben genannten Vorteile der erhöhten Steifigkeit und verminderten Geräuschentwicklung außergewöhnlich deutlich zutage.An internal combustion engine with a particularly low weight, which leads to reduced fuel consumption, in particular when used in a motor vehicle, is obtained by virtue of the crankcase consisting essentially of an aluminum alloy, according to another advantageous development of the invention; The term essentially means that some, a lower volume fraction constituents such as bearing bushes of the crankcase can be made of a different material. In an internal combustion engine having an aluminum alloy crankcase, moreover, the above-mentioned advantages of increased rigidity and reduced noise development are extremely evident.

Die Erfindung lässt zahlreiche Ausführungsformen zu. Zur weiteren Verdeutlichung ihres Grundprinzips ist eine davon in der Zeichnung dargestellt und wird nachfolgend beschrieben. Die Zeichnung zeigt in

Fig. 1
eine Teilansicht einer erfindungsgemäßen Brennkraftmaschine in Explosionsdarstellung und in
Fig. 2
die Brennkraftmaschine nach Figur 1 in einer weiteren, perspektivischen Teilansicht.
The invention allows numerous embodiments. To further clarify its basic principle, one of them is shown in the drawing and will be described below. The drawing shows in
Fig. 1
a partial view of an internal combustion engine according to the invention in an exploded view and in
Fig. 2
the internal combustion engine after FIG. 1 in a further perspective partial view.

In den beiden Figuren sind sich entsprechende Elemente mit gleichen Bezugszeichen versehen. Figur 1 zeigt einen Ausschnitt einer Brennkraftmaschine 1 mit einer Vorrichtung 2 zum Ausgleich von Massenwirkungen, die von einer hier nicht dargestellten Kurbelwelle der Brennkraftmaschine 1 antreibbar ist. Die Vorrichtung 2 zum Ausgleich von Massenwirkungen weist ein Ausgleichswellengehäuse mit einem als Lagerbrücke 4 ausgebildeten Gehäuseunterteil und einem als Gehäusedeckel 6 ausgebildeten Gehäuseoberteil auf. Die Brennkraftmaschine ist ein 4-Zylinder-Reihenmotor eines Personenkraftwagens.In the two figures, corresponding elements are provided with the same reference numerals. FIG. 1 shows a section of an internal combustion engine 1 with a device 2 for the compensation of mass effects, which is driven by a crankshaft of the internal combustion engine 1, not shown here. The device 2 for compensating for mass effects comprises a balance shaft housing with a lower housing part designed as a bearing bridge 4 and an upper housing part designed as a housing cover 6. The internal combustion engine is a 4-cylinder in-line engine of a passenger car.

Die Lagerbrücke 4 verbindet Lagerdeckel 8 von hier nicht dargestellten Kurbelwellenlagern der Kurbelwelle und wird mit den Lagerdeckeln 8 an ein Kurbelgehäuse 10 der Brennkraftmaschine 1 mittels Lagerdeckelschrauben 12 und Sechskantschrauben 14 befestigt. In der Lagerbrücke 4 sind zwei Ausgleichswellen 16, 18 gelagert, die über ein auf der Kurbelwelle angebrachtes Kettenrad 20, eine Kette 22 und ein auf der ersten Ausgleichswelle 16 angebrachtes zweites Kettenrad 24 angetrieben werden. Die Ausgleichswellen 16, 18 mit Ausgleichsmassen befinden sich mit ihren Schwerpunkten in der Mitte der Brennkraftmaschine 1 und in gleichem Achsabstand von der Kurbelwellenmitte. Der Gehäusedeckel 6 ist mit Bundschrauben 26 an der Lagerbrücke 4 befestigt. Die exakte Lage des Gehäusedeckels 6 zum die Lagerbrücke 4 bildenden Gehäuseunterteil wird mittels Passhülsen 28 sichergestellt.The bearing bridge 4 connects bearing cap 8 of crankshaft bearings of the crankshaft, not shown here, and is fastened with the bearing caps 8 to a crankcase 10 of the internal combustion engine 1 by means of bearing cap screws 12 and hexagon screws 14. In the bearing bridge 4, two balance shafts 16, 18 are mounted, which are driven by a mounted on the crankshaft sprocket 20, a chain 22 and a mounted on the first balance shaft 16 second sprocket 24. The balance shafts 16, 18 with balancing weights are located with their centers of gravity in the middle of the engine 1 and at the same distance from the center of the crankshaft. The housing cover 6 is fastened with collar bolts 26 on the bearing bracket 4. The exact position of the housing cover 6 to the bearing bracket 4 forming housing lower part is ensured by means of dowel sleeves 28.

Die erste Ausgleichswelle 16 wird an vier Lagerstellen 30, 32, 34, 36 radial gelagert, die zweite Ausgleichswelle 18 an drei Lagerstellen 38, 40, 42. Die Lagerungen der Ausgleichswellen 16, 18 bestehen aus Gleitlagern, wobei die Ausgleichswellen 16, 18 aufgrund der von ihnen erreichbaren hohen Drehzahlen (bis zu 13.600 1/min) in Lagerschalen 44 und Lagerbuchsen 46, 48 eingebettet sind. Die Gleitlager werden über hier nicht dargestellte Kanäle mit Öl aus dem Kurbelgehäuse 10 versorgt. Diese Kanäle verlaufen sowohl in der Lagerbrücke 4 als auch im Gehäusedeckel 6.The first balance shaft 16 is radially mounted at four bearing points 30, 32, 34, 36, the second balance shaft 18 at three bearings 38, 40, 42. The bearings of the balance shafts 16, 18 consist of plain bearings, wherein the balance shafts 16, 18 due to from them attainable high speeds (up to 13,600 1 / min) in bearing shells 44 and bearing bushes 46, 48 are embedded. The plain bearings are supplied with oil from the crankcase 10 via channels, not shown here. These channels extend both in the bearing bridge 4 and in the housing cover. 6

Der Antrieb der ersten Ausgleichswelle 16 erfolgt über das auf der Kurbelwelle angebrachte Kettenrad 20, das über die Kette 22 das auf der ersten Ausgleichswelle 16 angebrachte zweite Kettenrad 24 antreibt. Der Durchmesser der Kettenräder 20, 24 ist dabei so gewählt, dass die Drehzahl der ersten Ausgleichswelle 16 der doppelten Kurbelwellendrehzahl entspricht, das heißt die Übersetzung iK des Kettentriebs beträgt 0,5 (iK = 0,5). Ein auf der ersten Ausgleichswelle 16 angebrachtes erstes schrägverzahntes Zahnrad 50 bildet zusammen mit einem auf der zweiten Ausgleichswelle 18 angebrachten zweiten schrägverzahnten Zahnrad 52 eine erste Zahnradstufe, über die die zweite Ausgleichswelle 18 mit einer der ersten Ausgleichswelle 16 entsprechenden Drehzahl angetrieben wird. Somit beträgt die Übersetzung i1 der ersten Zahnradstufe 1 (i1 = 1).The drive of the first balance shaft 16 via the mounted on the crankshaft sprocket 20 which drives the chain 22 on the first balance shaft 16 mounted second sprocket 24. The diameter of the sprockets 20, 24 is chosen so that the speed of the first balancer shaft 16 is twice the crankshaft speed, that is, the ratio i K of the chain drive is 0.5 (i K = 0.5). A mounted on the first balancer shaft 16 first helical gear 50 forms together with a mounted on the second balance shaft 18 second helical gear 52, a first gear stage through which the second balance shaft 18 is driven with one of the first balance shaft 16 corresponding speed. Thus, the ratio i 1 of the first gear stage 1 (i 1 = 1).

Aufgrund der Schrägverzahnung der ersten Zahnradstufe entstehen an ihren Zahnrädern 50, 52 nicht nur Radialkräfte, sondern auch Axialkräfte, die über zusätzliche, hier nicht im Einzelnen dargestellte Axiallager aufgefangen werden. Die Axiallager befinden sich an den beiden Seiten der schrägverzahnten Zahnräder 50, 52, die jeweiligen Gegenflächen befinden sich an der Lagerbrücke 4 und am Gehäusedeckel 6. Durch die axiale Lagerung wird ein seitliches Verrutschen (Hin- und Herrutschen) sowie Klappern der Ausgleichswellen 16, 18 im Ausgleichswellengehäuse verhindert.Due to the helical gearing of the first gear stage arise on their gears 50, 52 not only radial forces, but also axial forces that are absorbed by additional, not shown in detail thrust bearing. The thrust bearings are located on the two sides of the helical gears 50, 52, the respective mating surfaces are located on the bearing bridge 4 and the housing cover 6. By the axial bearing is a lateral slipping (back and sideslip) and rattling of the balance shafts 16, 18th prevented in the balance shaft housing.

Die Vorrichtung 2 zum Ausgleich von Massenwirkungen weist ferner eine Ölpumpe 54 der Brennkraftmaschine 1 auf. Die Ölpumpe 54 ist eine verstellbare Außenzahnradpumpe, die in den Gehäusedeckel 6 des Ausgleichswellengehäuses mittels Bundschrauben 56 eingeschraubt ist. Der Antrieb der Ölpumpe 54 erfolgt durch die zweite Ausgleichswelle 18. Dazu ist auf der zweiten Ausgleichswelle 18 ein Antriebszahnrad 58 mit vergleichsweise kleinem Durchmesser angeordnet, in das ein auf einer Ölpumpenwelle 60 angeordnetes, einen größeren Durchmesser aufweisendes Eingangszahnrad 62 eingreift. Die Ölpumpenwelle 60 sowie erste und zweite Ausgleichswelle 16, 18 sind parallel zueinander angeordnet. Das Antriebszahnrad 58 und das Eingangszahnrad 62 gehören zu einer die Ölpumpe 54 antreibenden zweiten Zahnradstufe.The device 2 for compensating for mass effects further comprises an oil pump 54 of the internal combustion engine 1. The oil pump 54 is an adjustable external gear pump, which is screwed into the housing cover 6 of the balance shaft housing by means of collar bolts 56. The drive of the oil pump 54 is effected by the second balance shaft 18. For this purpose, a drive gear 58 is arranged with a comparatively small diameter on the second balance shaft 18, in which a arranged on an oil pump shaft 60, a larger diameter having input gear 62 engages. The oil pump shaft 60 and first and second balance shaft 16, 18 are arranged parallel to each other. The drive gear 58 and input gear 62 are associated with a second gear stage driving the oil pump 54.

Die Übersetzung der zweiten Zahnradstufe ist in diesem Ausführungsbeispiel derart gewählt, dass die Ölpumpenwelle 60 mit der Kurbelwellendrehzahl angetrieben wird, das heißt die Übersetzung i2 der zweiten Zahnradstufe beträgt 2 (i2 = 2). Die Drehzahl der Ölpumpenwelle 60 entspricht folglich der halben Drehzahl der beiden Ausgleichswellen 16, 18. Durch diese, von der zweiten Zahnradstufe bewerkstelligte Untersetzung ins Langsame wird ein hoher Wirkungsgrad der Ölpumpe 54 erreicht. Denkbar ist eine noch weitere Erhöhung des Wirkungsgrades der Ölpumpe 54 durch eine Absenkung der Drehzahl der Ölpumpenwelle 60 auf ein Niveau unterhalb der Drehzahl der Brennkraftmaschine 1.The ratio of the second gear stage is selected in this embodiment such that the oil pump shaft 60 is driven at the crankshaft speed, that is, the ratio i 2 of the second gear stage is 2 (i 2 = 2). The speed of the oil pump shaft 60 thus corresponds to half the speed of the two balancer shafts 16, 18. By this, accomplished by the second gear stage reduction in slow a high efficiency of the oil pump 54 is achieved. It is conceivable to further increase the efficiency of the oil pump 54 by lowering the speed of the oil pump shaft 60 to a level below the speed of the internal combustion engine. 1

Bei der im beschriebenen Ausführungsbeispiel gewählten Anordnung ist die Ölpumpe 54 das letzte Bauteil im Kraftfluss über die Ausgleichswellen 16, 18. Da die Ausgleichswellen 16, 18 während jeder Umdrehung der Kurbelwelle abwechselnd beschleunigt und verzögert werden, erfolgt grundsätzlich ein ständiger Anlagewechsel der Zähne der Zahnräder 50, 52 der ersten Zahnradstufe mit der Folge einer unerwünschten Geräuschentwicklung. Durch das von der Ölpumpe 54 bewirkte Bremsmoment wird in der hier gewählten Anordnung dieser grundsätzliche Anlagewechsel verhindert, die Zähne der Zahnräder 50, 52 befinden sich in immer gleicher Anlage, wodurch die Geräuschentwicklung minimiert wird. Das Gleiche gilt für die zweite Zahnradstufe mit dem Antriebszahnrad 58 auf der zweiten Ausgleichswelle 18 und dem Eingangszahnrad 62 auf der Ölpumpenwelle 60.In the arrangement chosen in the described embodiment, the oil pump 54 is the last component in the power flow through the balance shafts 16, 18. Since the balance shafts 16, 18 are alternately accelerated and decelerated during each revolution of the crankshaft, there is basically a constant change in the teeth of the gears 50th , 52 of the first gear stage with the consequence of unwanted noise. Due to the braking torque caused by the oil pump 54, this basic system change is prevented in the arrangement chosen here, the teeth of the gears 50, 52 are always in the same system, whereby the noise is minimized. The same applies to the second gear stage with the drive gear 58 on the second balance shaft 18 and the input gear 62 on the oil pump shaft 60th

In Figur 2 ist eine Teilansicht der Brennkraftmaschine 1 in zusammengebauter Ausführung gezeigt. Das Ausgleichswellengehäuse 64 ist hier geschlossen, der Gehäusedeckel 6 ist mit den Bundschrauben 26 auf die Lagerbrücke 4 aufgeschraubt, die wiederum mit den Sechskantschrauben 14 an Seitenwände 66, 68 des Kurbelgehäuses 10 angeschraubt ist. Hierzu weist die Lagerbrücke 4 seitliche Anbindungslaschen 70 auf, durch die die Sechskantschrauben 14 hindurchgreifen. Diese Anbindungslaschen 70 sind in einer zur Achse eines Zylinders der Brennkraftmaschine 1 parallelen Richtung, beispielhaft gekennzeichnet durch eine Gerade 72, biegeweich und in einer zur Kurbelwellenlängsachse parallelen Richtung, beispielhaft gekennzeichnet durch eine Gerade 74, biegesteif.In FIG. 2 a partial view of the internal combustion engine 1 is shown in assembled construction. The balance shaft housing 64 is closed here, the housing cover 6 is screwed with the collar bolts 26 on the bearing bracket 4, which in turn is screwed to the hexagonal screws 14 on side walls 66, 68 of the crankcase 10. For this purpose, the bearing bridge 4 has lateral connecting straps 70, through which the hexagon screws 14 extend. These connection straps 70 are exemplified in a direction parallel to the axis of a cylinder of the internal combustion engine 1 by a straight line 72, bendable and in a direction parallel to the crankshaft longitudinal axis, exemplified by a straight line 74, rigid.

Claims (11)

  1. Internal combustion engine with a device for balancing mass effects, which comprises a balancing shaft housing which is fastened to a crankcase and bears at least one balancing shaft which can be driven by a crankshaft, wherein in particular there is provided an oil pump which can be driven by the balancing shaft and is arranged on the balancing shaft housing and the crankshaft is mounted by crankshaft bearings, characterized in that at least a part of the balancing shaft housing (64) is formed as a bearing bridge (4) which connects the bearing covers (8) of the crankshaft bearings to one another and is fastened together with the bearing covers (8) on the crankcase (10).
  2. Internal combustion engine according to Claim 1, characterized in that the balancing shaft housing (64) has a housing lower part, which has connections to the bearing covers (8) and bears the bearing bridge (4), and a housing upper part formed as a housing cover (6).
  3. Internal combustion engine according to at least one of the preceding claims, characterized in that the bearing bridge (4) connects bearing covers (8) of all crankshaft bearings to one another and to a crankcase (10).
  4. Internal combustion engine according to at least one of the preceding claims, characterized in that the bearing bridge (4) is attached to side walls (66, 68) of the crankcase (10).
  5. Internal combustion engine according to Claim 4, characterized in that the bearing bridge (4) has lateral attachment tabs (70) which are screwed to the side walls (66, 68) of the crankcase (10).
  6. Internal combustion engine according to Claim 5, characterized in that the attachment tabs (70) are flexurally soft in a direction parallel to the axis of a cylinder of the internal combustion engine (1) and flexurally rigid in a direction parallel to the crankshaft longitudinal axis.
  7. Internal combustion engine according to at least one of the preceding claims, characterized in that a second balancing shaft (18) which can be driven by the first balancing shaft (16) is arranged.
  8. Internal combustion engine according to Claim 7, characterized in that the balancing shafts (16, 18) are connected to one another via a helical gearwheel mechanism.
  9. Internal combustion engine according to at least one of the preceding claims, characterized in that an oil pump (54) can be driven by a balancing shaft (16, 18).
  10. Internal combustion engine according to Claim 9, characterized in that a gearing is connected upstream of the oil pump (54) and steps down a rotational speed of the balancing shaft (18) which drives the oil pump (54).
  11. Internal combustion engine according to at least one of the preceding claims, characterized in that the crankcase (10) is substantially made of an aluminium alloy.
EP04028081A 2004-01-16 2004-11-26 Internal combustion engine Not-in-force EP1555405B1 (en)

Applications Claiming Priority (2)

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DE102004002277A DE102004002277A1 (en) 2004-01-16 2004-01-16 Internal combustion engine
DE102004002277 2004-01-16

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EP1555405B1 true EP1555405B1 (en) 2010-04-14

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Publication number Priority date Publication date Assignee Title
DE102008021528B4 (en) * 2008-04-30 2013-10-31 Ford Global Technologies, Llc An assembly for an internal combustion engine having an upper crankcase half, an oil pan and a support structure
DE102009025453B4 (en) * 2009-06-10 2019-12-05 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Balance shaft module
FR2987869B1 (en) * 2012-03-09 2014-04-18 Renault Sa THERMAL MOTOR COMPRISING INTERNAL SUPPORT ELEMENT INTEGRATED WITH OIL PUMP CREPINE

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Publication number Priority date Publication date Assignee Title
DE3824553C1 (en) * 1988-07-20 1989-02-02 Daimler-Benz Ag, 7000 Stuttgart, De Crankshaft bearing for an internal combustion engine
US5535643A (en) * 1993-11-12 1996-07-16 General Motors Corporation Anti-rattle engine balancer which drives associated oil pump
DE19750286A1 (en) * 1997-11-13 1999-05-20 Bayerische Motoren Werke Ag Drive arrangement for a second-order compensation device for a reciprocating piston internal combustion engine
DE10007660A1 (en) * 2000-02-19 2001-08-30 Daimler Chrysler Ag Device for balancing moments for IC engine comprises casing with bores for balance shafts and which contains cavity into which oil pump fits

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EP1555405A1 (en) 2005-07-20
DE502004011028D1 (en) 2010-05-27
DE102004002277A1 (en) 2005-08-11

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