EP1316683B1 - Oil pump combination for an internal combustion engine - Google Patents

Oil pump combination for an internal combustion engine Download PDF

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Publication number
EP1316683B1
EP1316683B1 EP02025133A EP02025133A EP1316683B1 EP 1316683 B1 EP1316683 B1 EP 1316683B1 EP 02025133 A EP02025133 A EP 02025133A EP 02025133 A EP02025133 A EP 02025133A EP 1316683 B1 EP1316683 B1 EP 1316683B1
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EP
European Patent Office
Prior art keywords
oil
pump
oil pump
gear
combustion engine
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EP02025133A
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German (de)
French (fr)
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EP1316683A2 (en
EP1316683A3 (en
Inventor
Kim Havemann
Frank Maier
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Dr Ing HCF Porsche AG
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Dr Ing HCF Porsche AG
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    • 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
    • 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
    • F01M2001/0269—Pressure lubrication using lubricating pumps characterised by the pump driving means driven by the crankshaft
    • 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
    • F01M1/12—Closed-circuit lubricating systems not provided for in groups F01M1/02 - F01M1/10
    • F01M2001/123—Closed-circuit lubricating systems not provided for in groups F01M1/02 - F01M1/10 using two or more pumps

Definitions

  • the invention is based on an oil pump combination for an internal combustion engine the features of the preamble of claim 1.
  • German patent application DE 100 14 368 is a Oil pump combination shown for an internal combustion engine, which consists of a in one Oil catch housing arranged two-stage main oil pump and a likewise consists of two-stage turbocharger suction pump, the latter outside of the Oil collection housing is flanged. Both pumps will work together over one Sprocket driven.
  • tandem pumps are furthermore known, in which Pump housing a plurality of pump stages are arranged and thus, for example, two Suction and pressure sides to supply different consumers can be formed.
  • an internal gear pump is known in the Two internal rotors are driven via a common drive shaft.
  • gear pumps are characterized by a small volume and a high power density are robust and suitable for tough conditions. The disadvantage is often too high Noise, which in the aforementioned double pumps due to their Multistage are particularly pronounced.
  • the object of the invention is therefore the oil pump combination described above to improve in terms of their noise.
  • a for noise reduction of the oil pump combination optimal design results when the two drive gears of the main oil pump and the oil suction pump for the turbocharger with each other by a 1 ⁇ 2 tooth and each other around each a 1 ⁇ 4 tooth angle offset from each other are arranged.
  • Volume flow pulsations can be further reduced if the outputs of two Pump stages are merged into a common output.
  • the oil trap housing shown in Fig. 1, hereinafter referred to as the oil pan 2 is in the assembled state with its flange 4 on a flange 6 of a Crankcase lower part 8, a so-called. Bedplate attached.
  • On the bottom of the Crankcase lower part 8 is designed as a double pump lubricating oil pump 10th attached.
  • a first oil collection chamber 12 is formed, in which the for the supply of lubricating oil accumulates in an oil sump.
  • an oil snorkel 14 is arranged, which has a first ⁇ labsaug réelle 16 to a suction side of a first pump stage 18 of the double oil pump 10 leads.
  • a second, rear oil collection chamber 20 is formed at whose lowest point is also an oil snorkel 22 is arranged, which has a second ⁇ labsaugtechnisch 24 with a suction side of a second pump stage 26 of the oil pump 10th connected is.
  • a plastic insert 28 is inserted, which is the two Oil collecting chambers 12 and 20 separated from each other.
  • the insert 28 serves as an oil barrier and prevents even when driving uphill of the motor vehicle that the lubricating oil the first oil collection chamber 12 in the crankcase and / or in the second Oil collecting space 20 can pass.
  • the lubricating oil pump 10 has a first, of two meshing gears 30 and 32 existing pump stage 18, wherein the gears 30 and 32 the Separate pump stage 18 in a suction side 34 and a pressure side 36.
  • the print side 36 leads via a pressure channel 37 to a pressure outlet 38, via which the consumer the internal combustion engine, such as. B. main or connecting rod bearing, supplied with lubricating oil become.
  • the second pump stage 26 also consists of two intermeshing Gears 40 and 42, which also the pump stage 26 analogous to the first pump stage Disconnect 18 in a suction side and a pressure side.
  • the housing of the oil pump 10 is constructed in three parts and consists of a basic housing 10 a and two am Basic housing attached cover elements 10b and 10c.
  • the top of the Basic housing 10a has an opening 44 which communicates with the pressure side of the second Pump stage 26 is connected.
  • the opening 44 is of a trough-like border 46 enclosed. That from the second oil collection chamber 20 via the second Oil suction line 24 sucked lubricating oil passes through the pressure side of the second Pump stage 26 and through the opening 44 in the riser formed trough-like border 46th There can be a certain amount of lubricating oil collected be before the over the trough-like border 46 overflowing part of Lubricating oil runs through the oil pump housing 10 in the first oil collection chamber 12.
  • the lubricating oil may defoam and those with a lower density Gas components of the lubricating oil via a not shown Crankcase breather be discharged to the outside.
  • the two drive gears 30 and 40 of the two pump stages 18 and 26 of the Lubricating oil pump 10 are arranged on a common axis 48, wherein the Drive gear 30 of the first pump stage 18 is shrunk on the axis 48, while the drive gear 40 of the second pump stage 26 via a groove / spring - Connection is fixed on the axis 48.
  • the two gears 30 and 40 are Angle offset arranged on the axis 48, such that they are by a 1 ⁇ 2 tooth offset from one another, so that the teeth of the gear 30 with the Tooth gaps of the gear 40 are brought into coincidence, and vice versa.
  • the two drive gears 30, 40 of the two pump stages 18 and 26 are over a sprocket 52, which in turn via a chain drive with a not shown Crankshaft gear is connected, driven.
  • a turbocharger - suction pump 54 flanged which also on the Sprocket 52 is driven. This is attached to the axis 48 Sprocket 52 provided with a driver 56, in which an intermediate piece 58 a Oldham - clutch 60 engages.
  • two housing halves 54a and 54b existing ⁇ labsaugpumpe 54 are also arranged two pump stages. A first Pump stage 62 is received in the housing half 54a, while a second Pump stage 64 in the housing half 54b recording takes place.
  • Both pump stages 62, 64 are separated and sealed by an intermediate plate 66.
  • the Housing half 54b has two inlet ports 68 and 70, wherein the inlet nozzle 68 leads to the suction side of the first pump stage 62, while the inlet nozzle 70 to Suction side of the second pump stage 64 leads.
  • the two Inlet stubs 68, 70 are connected to ⁇ labsaug réelleen, not shown, the each lead to a drive shaft of an exhaust gas turbocharger and over which the Drive shafts supplied lubricating oil is sucked.
  • the housing half 54a is provided with a Outlet opening 72 provided with the help of which via the two pump stages 62 and 64 extracted oil is returned to the oil sump of the oil pan 2 again.
  • These are the two pressure sides of the pump stages 62 and 64 via a in the intermediate plate 66th arranged breakthrough 74 connected to each other.
  • the two on a common Axis 76 arranged drive gears 78 and 82 are analogous to the Drive gears 30 and 40 of the main oil pump 10 offset by a 1 ⁇ 2 tooth arranged to each other, d.
  • the teeth of the drive gear 78 are connected to the Tooth gaps of the drive gear 82 brought into coincidence, and vice versa.
  • the Drive gear 78 is shrunk on the axis 76, while the drive gear 82 is rotatably mounted on the axle 76 via a pass / spring connection. That up an output gear 80 arranged on an axle 86 is simply plugged onto this while the output gear 84 is shrunk on the axle 86.
  • the bevel is advantageously in a range of 1 ⁇ 2 to 1 tooth, i. e.g. for pumping gears with 11 teeth in one Angular range from 0.5 * 360 ° / 11 to 1 * 360 ° / 11.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Lubrication Of Internal Combustion Engines (AREA)

Description

Die Erfindung geht aus von einer Ölpumpenkombination für eine Brennkraftmaschine nach den Merkmalen des Oberbegriffs des Anspruchs 1.The invention is based on an oil pump combination for an internal combustion engine the features of the preamble of claim 1.

In der noch nicht veröffentlichten deutschen Patentanmeldung DE 100 14 368 ist eine Ölpumpenkombination für eine Brennkraftmaschine dargestellt, die aus einer in einem Ölauffanggehäuse angeordneten zweistufigen Hauptölpumpe und einer ebenfalls zweistufig ausgebildeten Turbolader- Absaugpumpe besteht, wobei letztere außen an das Ölauffanggehäuse angeflanscht ist. Beide Pumpen werden gemeinsam über ein Kettenzahnrad angetrieben.In the not yet published German patent application DE 100 14 368 is a Oil pump combination shown for an internal combustion engine, which consists of a in one Oil catch housing arranged two-stage main oil pump and a likewise consists of two-stage turbocharger suction pump, the latter outside of the Oil collection housing is flanged. Both pumps will work together over one Sprocket driven.

Aus dem Stand der Technik sind weiterhin sog. Tandempumpen bekannt, bei denen im Pumpengehäuse mehrere Pumpenstufen angeordnet sind und damit beispielsweise zwei Saug- und Druckseiten zur Versorgung unterschiedlicher Verbraucher ausbildbar sind. Aus der DE 198 20 565 A1 ist beispielsweise eine Innenzahnradpumpe bekannt, bei der über eine gemeinsame Antriebswelle zwei Innenrotoren angetrieben sind. Zahnradpumpen zeichnen sich durch ein kleines Bauvolumen und eine hohe Leistungsdichte aus, sind robust und für harte Einsatzbedingungen geeignet. Nachteilig ist oft eine zu hohe Geräuschentwicklung, die bei den vorgenannten Doppelpumpen aufgrund ihrer Mehrstufigkeit besonders ausgeprägt sind.From the state of the art, so-called tandem pumps are furthermore known, in which Pump housing a plurality of pump stages are arranged and thus, for example, two Suction and pressure sides to supply different consumers can be formed. From DE 198 20 565 A1, for example, an internal gear pump is known in the Two internal rotors are driven via a common drive shaft. gear pumps are characterized by a small volume and a high power density are robust and suitable for tough conditions. The disadvantage is often too high Noise, which in the aforementioned double pumps due to their Multistage are particularly pronounced.

Aufgabe der Erfindung ist es daher, die eingangs beschriebene Ölpumpenkombination hinsichtlich ihrer Geräuschentwicklung zu verbessern.The object of the invention is therefore the oil pump combination described above to improve in terms of their noise.

Die Lösung der Aufgabe erfolgt durch die im Anspruch 1 angegebenen Merkmale.The solution of the problem is achieved by the features specified in claim 1.

Dadurch, dass die Zahnradpaare der Hauptölpumpe und der Ölabsaugpumpe für die Abgasturbolader sowohl untereinander als auch zueinander drehwinkelversetzt angeordnet sind, findet eine zeitversetzte Vergrößerung bzw. Verkleinerung der Verdrängerräume statt. Die drehwinkelversetzte Anordnung der Zahnräder führt zu einer Reduzierung des Geräuschpegels, da die maximalen Geräuschamplituden der einzelnen Pumpenstufen phasenverschoben auftreten und sich somit die Maximas nicht überlagern, was wiederum zu einer Geräuschreduzierung der Ölpumpenkombination führt.The fact that the gear pairs of the main oil pump and the Ölabsaugpumpe for Exhaust gas turbocharger both with each other and each other with angular displacement are arranged, finds a time-delayed increase or decrease in the Displacement rooms instead. The rotational angle offset arrangement of the gears leads to a Reduction of the noise level, as the maximum noise amplitudes of each Pump stages out of phase and thus do not overlap the Maximas, which in turn leads to a noise reduction of the oil pump combination.

In den Unteransprüchen sind weitere vorteilhafte Ausgestaltungen und Verbesserungen der erfindungsgemäßen Ölpumpenkombination enthalten.In the subclaims are further advantageous embodiments and improvements contain the oil pump combination according to the invention.

Eine zur Geräuschreduzierung der Ölpumpenkombination optimaler Ausgestaltung ergibt sich, wenn die beiden Antriebszahnräder der Hauptölpumpe und der Ölabsaugpumpe für den Abgasturbolader untereinander um jeweils einen ½ Zahn und zueinander um jeweils einen ¼ Zahn drehwinkelversetzt zueinander angeordnet sind.A for noise reduction of the oil pump combination optimal design results when the two drive gears of the main oil pump and the oil suction pump for the turbocharger with each other by a ½ tooth and each other around each a ¼ tooth angle offset from each other are arranged.

Volumenstrompulsationen können weiter reduziert werden, wenn die Ausgänge von zwei Pumpenstufen zu einem gemeinsamen Ausgang zusammengeführt sind.Volume flow pulsations can be further reduced if the outputs of two Pump stages are merged into a common output.

Ein Ausführungsbeispiel der Erfindung ist in der nachfolgenden Beschreibung und Zeichnung näher erläutert.An embodiment of the invention is described in the following description and Drawing explained in more detail.

Es zeigen:

Fig. 1
eine Draufsicht auf eine Ölauffangvorrichtung,
Fig. 2
eine an ein Kurbelgehäuseunterteil angeflanschte Hauptölpumpe,
Fig. 3
die Hauptölpumpe mit angeflanschter Ölabsaugpumpe für zwei Abgasturbolader,
Fig. 4
eine Ansicht auf das Grundgehäuse der Hauptölpumpe,
Fig. 5
eine Ansicht auf das Grundgehäuse der Hauptölpumpe ohne eingesetzte Zahnräder,
Fig. 6
eine Darstellung der Zahnradpaare der Hauptölpumpe und der Ölabsaugpumpe,
Fig. 7
eine Ansicht auf die Zahnradpaarungen,
Fig. 8
eine erste Seitenansicht der Ölabsaugpumpe,
Fig. 9
eine zweite Seitenansicht der Ölabsaugpumpe und
Fig. 10
eine Ansicht auf eine Pumpenstufe der Ölabsaugpumpe.
Show it:
Fig. 1
a top view of an oil catcher,
Fig. 2
a main oil pump flanged to a crankcase lower part,
Fig. 3
the main oil pump with flanged oil suction pump for two turbochargers,
Fig. 4
a view of the main housing of the main oil pump,
Fig. 5
a view of the main housing of the main oil pump without gears,
Fig. 6
a representation of the gear pairs of the main oil pump and the Ölabsaugpumpe,
Fig. 7
a view of the gear pairs,
Fig. 8
a first side view of the oil suction pump,
Fig. 9
a second side view of the oil suction and
Fig. 10
a view of a pump stage of Ölabsaugpumpe.

Beschreibung des AusführungsbeispielsDescription of the embodiment

Das in Fig. 1 dargestellte Ölauffanggehäuse, im folgenden als Ölwanne 2 bezeichnet, ist im zusammengebauten Zustand mit seiner Flanschfläche 4 an einer Flanschfläche 6 eines Kurbelgehäuseunterteils 8, einem sog. bedplate, befestigt. Auf der Unterseite des Kurbelgehäuseunterteils 8 ist eine als Doppelpumpe ausgebildete Schmierölpumpe 10 befestigt. In der Ölwanne 2 ist ein erster Ölsammelraum 12 ausgebildet, in dem sich das für die Schmierölversorgung notwendige Öl in einem Ölsumpf ansammelt. Im ersten Ölsammelraum 12 ist ein Ölschnorchel 14 angeordnet, der über eine erste Ölabsaugleitung 16 zu einer Saugseite einer ersten Pumpenstufe 18 der Doppelölpumpe 10 führt. In der Ölwanne 2 ist ein zweiter, hinterer Ölsammelraum 20 ausgebildet, an dessen tiefster Stelle ebenfalls ein Ölschnorchel 22 angeordnet ist, der über eine zweite Ölabsaugleitung 24 mit einer Saugseite einer zweiten Pumpenstufe 26 der Ölpumpe 10 verbunden ist.The oil trap housing shown in Fig. 1, hereinafter referred to as the oil pan 2, is in the assembled state with its flange 4 on a flange 6 of a Crankcase lower part 8, a so-called. Bedplate attached. On the bottom of the Crankcase lower part 8 is designed as a double pump lubricating oil pump 10th attached. In the oil pan 2, a first oil collection chamber 12 is formed, in which the for the supply of lubricating oil accumulates in an oil sump. In the first Oil collecting space 12, an oil snorkel 14 is arranged, which has a first Ölabsaugleitung 16 to a suction side of a first pump stage 18 of the double oil pump 10 leads. In the oil pan 2, a second, rear oil collection chamber 20 is formed at whose lowest point is also an oil snorkel 22 is arranged, which has a second Ölabsaugleitung 24 with a suction side of a second pump stage 26 of the oil pump 10th connected is.

In die Ölwanne 2 ist ein Kunststoff - Einlegeteil 28 eingesetzt, das die beiden Ölsammelräume 12 und 20 voneinander trennt. Das Einlegeteil 28 dient als Ölbarriere und verhindert auch bei Steigungsfahrten des Kraftfahrzeugs, dass das Schmieröl aus dem ersten Ölsammelraum 12 in den Kurbelraum und/oder in den zweiten Ölsammelraum 20 übertreten kann. Im zweiten Ölsammelraum 20 wird das Schmieröl von den Hauptlagern der Kurbelwelle und das Schmieröl aus den nicht dargestellten Spritzdüsen für die Kolbenkühlung aufgefangen und über die zweite Ölabsaugleitung 24 in den ersten Ölsammelraum 12 zurückgefördert.In the oil pan 2, a plastic insert 28 is inserted, which is the two Oil collecting chambers 12 and 20 separated from each other. The insert 28 serves as an oil barrier and prevents even when driving uphill of the motor vehicle that the lubricating oil the first oil collection chamber 12 in the crankcase and / or in the second Oil collecting space 20 can pass. In the second oil collection chamber 20, the lubricating oil from the main bearings of the crankshaft and the lubricating oil from the not shown Collected spray nozzles for the piston cooling and the second Ölabsaugleitung 24 in the first oil collection chamber 12 fed back.

Die Schmierölpumpe 10 weist eine erste, aus zwei ineinander kämmenden Zahnrädern 30 und 32 bestehende Pumpenstufe 18 auf, wobei die Zahnräder 30 und 32 die Pumpenstufe 18 in eine Saugseite 34 und eine Druckseite 36 abtrennen. Die Druckseite 36 führt über einen Druckkanal 37 zu einem Druckausgang 38, über den die Verbraucher der Brennkraftmaschine, wie z. B. Haupt- oder Pleuellager, mit Schmieröl versorgt werden. Die zweite Pumpenstufe 26 besteht ebenfalls aus zwei ineinander kämmenden Zahnrädern 40 und 42, die ebenfalls die Pumpenstufe 26 analog zur ersten Pumpenstufe 18 in eine Saugseite und eine Druckseite abtrennen. Das Gehäuse der Ölpumpe 10 ist dreiteilig aufgebaut und besteht aus einem Grundgehäuse 10a und zwei am Grundgehäuse befestigten Deckelelementen 10b und 10c. Die Oberseite des Grundgehäuses 10a weist eine Öffnung 44 auf, die mit der Druckseite der zweiten Pumpenstufe 26 verbunden ist. Die Öffnung 44 ist von einer wannenartigen Umrandung 46 umschlossen. Das aus dem zweiten Ölsammelraum 20 über die zweite Ölabsaugleitung 24 abgesaugte Schmieröl gelangt über die Druckseite der zweiten Pumpenstufe 26 und über die Öffnung 44 in die als Steigkamin ausgebildete wannenartige Umrandung 46. Dort kann eine gewisse Schmierölmenge aufgefangen werden, bevor der über die wannenartige Umrandung 46 übertretende Teil des Schmieröls über das Ölpumpengehäuse 10 in den ersten Ölsammelraum 12 abläuft. Während der Zeit, in der das Schmieröl in der wannenartigen Umrandung 46 gehalten ist, kann sich das Schmieröl entschäumen und die mit einer geringeren Dichte versehenen Gasbestandteile des Schmieröls über eine nicht weiter dargestellte Kurbelgehäuseentlüftungseinrichtung nach außen abgeführt werden.The lubricating oil pump 10 has a first, of two meshing gears 30 and 32 existing pump stage 18, wherein the gears 30 and 32 the Separate pump stage 18 in a suction side 34 and a pressure side 36. The print side 36 leads via a pressure channel 37 to a pressure outlet 38, via which the consumer the internal combustion engine, such as. B. main or connecting rod bearing, supplied with lubricating oil become. The second pump stage 26 also consists of two intermeshing Gears 40 and 42, which also the pump stage 26 analogous to the first pump stage Disconnect 18 in a suction side and a pressure side. The housing of the oil pump 10 is constructed in three parts and consists of a basic housing 10 a and two am Basic housing attached cover elements 10b and 10c. The top of the Basic housing 10a has an opening 44 which communicates with the pressure side of the second Pump stage 26 is connected. The opening 44 is of a trough-like border 46 enclosed. That from the second oil collection chamber 20 via the second Oil suction line 24 sucked lubricating oil passes through the pressure side of the second Pump stage 26 and through the opening 44 in the riser formed trough-like border 46th There can be a certain amount of lubricating oil collected be before the over the trough-like border 46 overflowing part of Lubricating oil runs through the oil pump housing 10 in the first oil collection chamber 12. During the time in which the lubricating oil is held in the trough-like border 46, The lubricating oil may defoam and those with a lower density Gas components of the lubricating oil via a not shown Crankcase breather be discharged to the outside.

Die beiden Antriebszahnräder 30 und 40 der beiden Pumpenstufen 18 und 26 der Schmierölpumpe 10 sind auf einer gemeinsamen Achse 48 angeordnet, wobei das Antriebszahnrad 30 der ersten Pumpenstufe 18 auf der Achse 48 aufgeschrumpft ist, während das Antriebszahnrad 40 der zweiten Pumpenstufe 26 über eine Nut/Feder - Verbindung auf der Achse 48 fixiert ist. Die beiden Zahnräder 30 und 40 sind drehwinkelversetzt auf der Achse 48 angeordnet, dergestalt, dass sie um einen ½ Zahn versetzt zueinander angeordnet sind, so dass die Zähne des Zahnrades 30 mit den Zahnlücken des Zahnrades 40 in Überdeckung gebracht sind, und umgekehrt. Analog dazu sind die auf einer gemeinsamen Achse 50 angeordneten Abtriebszahnräder 32 und 42 um einen ½ Zahn drehwinkelversetzt zueinander angeordnet, so dass die Zähne des Zahnrades 32 mit den Zahnlücken des Zahnrades 42 bzw. umgekehrt in Überdeckung gebracht sind. Während das Zahnrad 32 wiederum mit der Achse 50 fest verbunden ist, ist das Zahnrad 42 lediglich auf die Achse 50 aufgeschoben. Als Alternative ist eine Ausführung der Achse 50 als feststehender Bolzen denkbar, der im Gehäuse eingepresst ist. In diesem Fall sind sowohl das Zahnrad 32 als auch das Zahnrad 42 lediglich auf die Achse 50 aufgeschoben und drehbar gelagert.The two drive gears 30 and 40 of the two pump stages 18 and 26 of the Lubricating oil pump 10 are arranged on a common axis 48, wherein the Drive gear 30 of the first pump stage 18 is shrunk on the axis 48, while the drive gear 40 of the second pump stage 26 via a groove / spring - Connection is fixed on the axis 48. The two gears 30 and 40 are Angle offset arranged on the axis 48, such that they are by a ½ tooth offset from one another, so that the teeth of the gear 30 with the Tooth gaps of the gear 40 are brought into coincidence, and vice versa. Analogous These are arranged on a common axis 50 driven gears 32 and 42 arranged by a ½ tooth angle offset from each other, so that the teeth of the Gear 32 with the tooth gaps of the gear 42 and vice versa in coverage are brought. While the gear 32 is in turn fixed to the axle 50, the gear 42 is merely pushed onto the axis 50. As an alternative, one Design of the axis 50 as a fixed bolt conceivable that pressed into the housing is. In this case, both the gear 32 and the gear 42 are only on the Axis 50 postponed and stored rotatably.

Die beiden Antriebszahnräder 30, 40 der beiden Pumpenstufen 18 und 26 werden über ein Kettenzahnrad 52, das wiederum über einen Kettentrieb mit einem nicht dargestellten Kurbelwellenzahnrad verbunden ist, angetrieben. An der Stirnseite der Ölwanne 2 ist weiterhin eine Turbolader - Absaugpumpe 54 angeflanscht, die ebenfalls über das Kettenzahnrad 52 angetrieben ist. Dazu ist das an der Achse 48 befestigte Kettenzahnrad 52 mit einem Mitnehmer 56 versehen, in den ein Zwischenstück 58 einer Oldham - Kupplung 60 eingreift. In der aus zwei Gehäusehälften 54a und 54b bestehenden Ölabsaugpumpe 54 sind ebenfalls zwei Pumpenstufen anordnet. Eine erste Pumpenstufe 62 ist in der Gehäusehälfte 54a aufgenommen, während eine zweite Pumpenstufe 64 in der Gehäusehälfte 54b Aufnahme findet. Beide Pumpenstufen 62, 64 sind durch eine Zwischenplatte 66 voneinander getrennt und abgedichtet. Die Gehäusehälfte 54b weist zwei Eintrittsstutzen 68 und 70 auf, wobei der Eintrittsstutzen 68 zur Saugseite der ersten Pumpenstufe 62 führt, während der Eintrittsstutzen 70 zur Saugseite der zweiten Pumpenstufe 64 führt. Zur Anbindung des Eintrittstutzens 68 an die Saugseite der ersten Pumpenstufe 62 ist in der Zwischenplatte 66 eine mit den Eintrittsstutzen 68 korrespondierende Öffnung 69 vorgesehen, die mit Hilfe eines Dichtrings 71 gegenüber der zweiten Pumpenstufe 64 abgedichtet ist. Die beiden Eintrittsstutzen 68, 70 sind mit nicht dargestellten Ölabsaugleitungen verbunden, die jeweils zu einer Antriebswelle eines Abgasturboladers führen und über die das den Antriebswellen zugeführte Schmieröl abgesaugt wird. Die Gehäusehälfte 54a ist mit einer Austrittsöffnung 72 versehen, mit dessen Hilfe das über die beiden Pumpenstufen 62 und 64 abgesaugte Öl wieder in den Ölsumpf der Ölwanne 2 zurückgeführt wird. Dazu sind die beiden Druckseiten der Pumpenstufen 62 und 64 über einen in der Zwischenplatte 66 angeordneten Durchbruch 74 miteinander verbunden. Die beiden auf einer gemeinsamen Achse 76 angeordneten Antriebszahnräder 78 und 82 sind analog zu den Antriebszahnrädern 30 und 40 der Hauptölpumpe 10 um einen ½ Zahn versetzt zueinander angeordnet, d. h. die Zähne des Antriebszahnrades 78 sind mit den Zahnlücken des Antriebszahnrades 82 in Überdeckung gebracht, und umgekehrt. Analog dazu sind die beiden Abtriebszahnräder 80 und 84 der ersten und zweiten Pumpenstufe der Ölabsaugpumpe 54 um einen halben Zahn versetzt zueinander angeordnet. Das Antriebszahnrad 78 ist auf der Achse 76 aufgeschrumpft, während das Antriebszahnrad 82 über eine Pass/Feder - Verbindung drehfest auf der Achse 76 angeordnet ist. Das auf einer Achse 86 angeordnete Abtriebszahnrad 80 ist lediglich auf dieser aufgesteckt, während das Abtriebszahnrad 84 auf der Achse 86 aufgeschrumpft ist.The two drive gears 30, 40 of the two pump stages 18 and 26 are over a sprocket 52, which in turn via a chain drive with a not shown Crankshaft gear is connected, driven. At the front of the oil pan 2 is Furthermore, a turbocharger - suction pump 54 flanged, which also on the Sprocket 52 is driven. This is attached to the axis 48 Sprocket 52 provided with a driver 56, in which an intermediate piece 58 a Oldham - clutch 60 engages. In the case of two housing halves 54a and 54b existing Ölabsaugpumpe 54 are also arranged two pump stages. A first Pump stage 62 is received in the housing half 54a, while a second Pump stage 64 in the housing half 54b recording takes place. Both pump stages 62, 64 are separated and sealed by an intermediate plate 66. The Housing half 54b has two inlet ports 68 and 70, wherein the inlet nozzle 68 leads to the suction side of the first pump stage 62, while the inlet nozzle 70 to Suction side of the second pump stage 64 leads. To connect the inlet connector 68 at the suction side of the first pump stage 62 is in the intermediate plate 66 a with the Eintrittsstutzen 68 corresponding opening 69 is provided, which by means of a Sealing ring 71 is sealed relative to the second pump stage 64. The two Inlet stubs 68, 70 are connected to Ölabsaugleitungen, not shown, the each lead to a drive shaft of an exhaust gas turbocharger and over which the Drive shafts supplied lubricating oil is sucked. The housing half 54a is provided with a Outlet opening 72 provided with the help of which via the two pump stages 62 and 64 extracted oil is returned to the oil sump of the oil pan 2 again. These are the two pressure sides of the pump stages 62 and 64 via a in the intermediate plate 66th arranged breakthrough 74 connected to each other. The two on a common Axis 76 arranged drive gears 78 and 82 are analogous to the Drive gears 30 and 40 of the main oil pump 10 offset by a ½ tooth arranged to each other, d. H. the teeth of the drive gear 78 are connected to the Tooth gaps of the drive gear 82 brought into coincidence, and vice versa. Analogous to the two output gears 80 and 84 of the first and second pump stage the Ölabsaugpumpe 54 offset by half a tooth to each other. The Drive gear 78 is shrunk on the axis 76, while the drive gear 82 is rotatably mounted on the axle 76 via a pass / spring connection. That up an output gear 80 arranged on an axle 86 is simply plugged onto this while the output gear 84 is shrunk on the axle 86.

Betrachtet man die Gesamtanordnung der Zahnradpaare der Hauptölpumpe 10 und der Ölabsaugpumpe 54 für die Abgasturbolader so wird aus Fig. 7 ersichtlich, dass die Antriebszahnräder 30, 40 gegenüber den Antriebszahnrädern 78 und 82 der Ölabsaugpumpe 54 ebenfalls drehwinkelversetzt zueinander angeordnet sind. In diesem Fall sind die Antriebszahnräder 30, 40 der Hauptölpumpe 10 gegenüber den Antriebszahnrädern 78, 82 der Ölabsaugpumpe 54 um einen ¼ Zahn zueinander drehwinkelversetzt angeordnet. Im vorliegenden Ausführungsbeispiel weisen die Zahnräder der Hauptölpumpe 10 und der Ölabsaugpumpe 54 für die Abgasturbolader elf Zähne auf. Damit ergibt sich eine drehwinkelversetzte Anordnung der beiden Antriebszahnräder 30 und 40 der Hauptölpumpe 10 und der beiden Antriebszahnräder 78 und 82 der Ölabsaugpumpe 54 von ca. 16,4° untereinander, während die Antriebszahnräder 30, 40 gegenüber den Antriebszahnrädern 78, 82 um ca. 8,2° drehwinkelversetzt zueinander angeordnet sind. Durch eine derartige Anordnung der vier Zahnradsätze treten die periodischen Zahneingriffsimpulse phasenverschoben auf, so daß sich die maximalen Geräuschamplituden des jeweiligen Zahneingriffs nicht überlagern, was zu einer Geräuschreduzierung der Ölpumpenkombination insgesamt führt. Considering the overall arrangement of the gear pairs of the main oil pump 10 and the Ölabsaugpumpe 54 for the exhaust gas turbocharger so it is apparent from Fig. 7 that the Drive gears 30, 40 opposite the drive gears 78 and 82 of the Ölabsaugpumpe 54 are also arranged offset angle to each other. In this Case are the drive gears 30, 40 of the main oil pump 10 with respect to the Drive gears 78, 82 of Ölabsaugpumpe 54 by a ¼ tooth to each other arranged offset in angle of rotation. In the present embodiment, the Gears of the main oil pump 10 and the Ölabsaugpumpe 54 for the exhaust gas turbocharger eleven Teeth on. This results in a rotational angle offset arrangement of the two Drive gears 30 and 40 of the main oil pump 10 and the two drive gears 78 and 82 of the Ölabsaugpumpe 54 of about 16.4 ° with each other, while the Drive gears 30, 40 opposite the drive gears 78, 82 by about 8.2 ° are arranged offset in angle to each other. By such an arrangement of the four Gear sets, the periodic tooth engagement pulses occur out of phase, so that the maximum noise amplitudes of the respective tooth engagement do not overlap, resulting in a noise reduction of the oil pump combination overall.

Als weitere Maßnahmen zur Geräuschreduzierung in der Hauptölpumpe 10 sind, wie in Fig. 5 dargestellt, im Gehäuseteil 10a im Bereich des Zahnradsatzes 30, 32 sog. Druckentlastungsnieren 88 vorgesehen. Darüber hinaus ist im Bereich der ineinander kämmenden Zahnräder 30 und 32 ein Mittelsteg 90 vorgesehen, dessen obere Begrenzungskante 90a im wesentlichen in seiner Verlängerung durch die Mitte der beiden Lager 92 und 94 für die Achsen 48 und 50 verläuft. Oberhalb der oberen Begrenzungskante 90a sind zwei zu den Lagern 92 und 94 führende Nuten 96 und 98 vorgesehen, die einerseits die Lagerstellen mit Schmieröl versorgen und andererseits der Abfuhr von sog. Quetschöl dienen. Weiterhin sind die Wände W1, W2, W3 und W4 (siehe Fig. 5), über die das zu fördernde Öl zwischen den Zähnen abgeschlossen (Saugseite) bzw. wieder freigegeben wird (Druckseite), abgeschrägt, damit der jeweilige Vorgang nicht schlagartig, sondern gleichmäßig stattfindet. Die Abschrägung verläuft vorteilhaft in einem Bereich von ½ bis 1 Zahn, d.h. z.B. bei Pumpenrädern mit 11 Zähnen in einem Winkelbereich von 0.5*360°/11 bis 1*360°/11. Durch die vier zuletzt genannten Maßnahmen wird ebenfalls zu einer Geräuschreduzierung der Hauptölpumpe 10 und damit zu einer Geräuschreduzierung der gesamten Ölpumpenkombination beigetragen.As further measures for noise reduction in the main oil pump 10, as in Fig. 5, in the housing part 10a in the region of the gear set 30, 32 so-called. Pressure relief kidneys 88 provided. In addition, in the area of one another meshing gears 30 and 32, a central web 90 is provided, the upper Bounding edge 90a substantially in its extension through the middle of the two Bearings 92 and 94 for the axles 48 and 50 runs. Above the top The boundary edge 90a is two grooves 96 and 98 leading to the bearings 92 and 94 provided, on the one hand supply the bearings with lubricating oil and on the other hand the Removal of so-called squeeze oil serve. Furthermore, the walls W1, W2, W3 and W4 (see Fig. 5), over which the oil to be delivered between the teeth completed (suction side) or released again (print page), bevelled, so that the respective process not abrupt, but takes place evenly. The bevel is advantageously in a range of ½ to 1 tooth, i. e.g. for pumping gears with 11 teeth in one Angular range from 0.5 * 360 ° / 11 to 1 * 360 ° / 11. By the four last mentioned Measures will also be to a noise reduction of the main oil pump 10 and thus contributing to noise reduction of the entire oil pump combination.

Claims (2)

  1. An oil-pump combination for a supercharged internal-combustion engine which is provided with two rows of cylinders and which has the following features:
    a main oil pump (10), provided with a pump housing, for drawing away the lubricating oil present in an oil-collecting device (2),
    at least two pumping chambers are formed in the pump housing, wherein a pair of intermeshing toothed wheels (30, 32 and 40, 42 respectively) is arranged in each pumping chamber in order to form one pumping stage in each case,
    an oil-suction pump (54), provided with two pumping chambers, for the exhaust-gas turbocharger of the internal-combustion engine, wherein a pair of intermeshing toothed wheels (78, 80 and 82, 84 respectively) is arranged in each pumping chamber in order to form one pumping stage (62, 64) in each case,
    the two driving toothed wheels (30, 40) of the main oil pump (10) and the two driving toothed wheels (78, 82) of the oil-suction pump (54) are arranged offset at an angle of rotation both between themselves and with respect to the others in each case.
  2. An oil-pump combination according to Claim 1, characterized in that the two driving toothed wheels (30, 40) of the main oil pump (10) and of the oil-suction pump (54) are arranged offset at an angle of rotation by 1/2 a tooth between themselves and by a 1/4 of a tooth with respect to the others in each case.
EP02025133A 2001-12-01 2002-11-09 Oil pump combination for an internal combustion engine Expired - Lifetime EP1316683B1 (en)

Applications Claiming Priority (2)

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DE10159088A DE10159088A1 (en) 2001-12-01 2001-12-01 Oil pump combination for an internal combustion engine
DE10159088 2001-12-01

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EP1316683A2 EP1316683A2 (en) 2003-06-04
EP1316683A3 EP1316683A3 (en) 2004-01-21
EP1316683B1 true EP1316683B1 (en) 2005-05-25

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US7674095B2 (en) 2000-12-12 2010-03-09 Borgwarner Inc. Variable displacement vane pump with variable target regulator
US7726948B2 (en) 2002-04-03 2010-06-01 Slw Automotive Inc. Hydraulic pump with variable flow and variable pressure and electric control

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US6896489B2 (en) 2000-12-12 2005-05-24 Borgwarner Inc. Variable displacement vane pump with variable target regulator
DE102005029086B4 (en) * 2005-06-23 2016-06-16 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Oil pump for an internal combustion engine
DE102005029084B4 (en) 2005-06-23 2022-11-03 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Oil pump for an internal combustion engine
GB0515494D0 (en) 2005-07-28 2005-08-31 Bamford Excavators Ltd Fluid pumping apparatus
DE102006027660A1 (en) * 2006-06-14 2007-12-20 Schwäbische Hüttenwerke Automotive GmbH & Co. KG Oil pump device for an internal combustion engine with an oil pan
US20120051950A1 (en) * 2010-08-27 2012-03-01 Chang Chun-Hsien Engine oil pump provided automatic adjustment of oil supply amount
DE102021116160A1 (en) * 2021-06-22 2022-12-22 Fte Automotive Gmbh Gear pump and prime mover

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DE19820565A1 (en) 1997-06-21 1999-01-21 Bayerische Motoren Werke Ag Geared pump for use in vehicles
DE10014368B4 (en) * 2000-03-23 2004-05-19 Dr.Ing.H.C. F. Porsche Ag Oil collecting device for an internal combustion engine
DE10144693B4 (en) * 2001-09-11 2012-06-21 Volkswagen Ag Gear pump for lubricating oil supply

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7674095B2 (en) 2000-12-12 2010-03-09 Borgwarner Inc. Variable displacement vane pump with variable target regulator
US7726948B2 (en) 2002-04-03 2010-06-01 Slw Automotive Inc. Hydraulic pump with variable flow and variable pressure and electric control

Also Published As

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DE50203186D1 (en) 2005-06-30
DE10159088A1 (en) 2003-06-18
EP1316683A2 (en) 2003-06-04
EP1316683A3 (en) 2004-01-21

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