EP0406527B1 - Driving system for two oil pumps of an internal combustion engine with reciprocating pistons - Google Patents

Driving system for two oil pumps of an internal combustion engine with reciprocating pistons Download PDF

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Publication number
EP0406527B1
EP0406527B1 EP90106688A EP90106688A EP0406527B1 EP 0406527 B1 EP0406527 B1 EP 0406527B1 EP 90106688 A EP90106688 A EP 90106688A EP 90106688 A EP90106688 A EP 90106688A EP 0406527 B1 EP0406527 B1 EP 0406527B1
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EP
European Patent Office
Prior art keywords
crankshaft
oil pump
drive
combustion engine
gearwheel
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP90106688A
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German (de)
French (fr)
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EP0406527A1 (en
Inventor
Herbert Dipl.-Ing. Ampferer (Fh)
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Dr Ing HCF Porsche AG
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Dr Ing HCF Porsche AG
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Publication of EP0406527A1 publication Critical patent/EP0406527A1/en
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/02—Valve drive
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/02—Valve drive
    • F01L1/022—Chain drive
    • 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
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B67/00—Engines characterised by the arrangement of auxiliary apparatus not being otherwise provided for, e.g. the apparatus having different functions; Driving auxiliary apparatus from engines, not otherwise provided for
    • F02B67/04—Engines characterised by the arrangement of auxiliary apparatus not being otherwise provided for, e.g. the apparatus having different functions; Driving auxiliary apparatus from engines, not otherwise provided for of mechanically-driven auxiliary apparatus
    • F02B67/06—Engines characterised by the arrangement of auxiliary apparatus not being otherwise provided for, e.g. the apparatus having different functions; Driving auxiliary apparatus from engines, not otherwise provided for of mechanically-driven auxiliary apparatus driven by means of chains, belts, or like endless members
    • 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
    • F02B75/16—Engines characterised by number of cylinders, e.g. single-cylinder engines
    • F02B75/18—Multi-cylinder engines
    • F02B75/22—Multi-cylinder engines with cylinders in V, fan, or star arrangement
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/02—Valve drive
    • F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
    • F01L1/047—Camshafts
    • F01L1/053—Camshafts overhead type
    • F01L2001/0537—Double overhead camshafts [DOHC]
    • 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
    • F02B75/16—Engines characterised by number of cylinders, e.g. single-cylinder engines
    • F02B75/18—Multi-cylinder engines
    • F02B2075/1804—Number of cylinders
    • F02B2075/1832—Number of cylinders eight
    • 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
    • F02B2275/00—Other engines, components or details, not provided for in other groups of this subclass
    • F02B2275/08—Endless member is a chain
    • 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
    • F02B2275/00—Other engines, components or details, not provided for in other groups of this subclass
    • F02B2275/18—DOHC [Double overhead camshaft]

Definitions

  • the invention relates to a device for driving two oil pumps arranged on a reciprocating piston internal combustion engine according to the preamble of claim 1, which is based on DE-A-26 20 480.
  • a lubricating oil supply for an internal combustion engine which has a main oil pump for supplying a main lubricating oil circuit and a second oil pump for a secondary lubricating oil circuit of auxiliary machines.
  • EP-PS 163 046 describes a hydraulic device for adjusting the angle of two camshafts, in which an oil pump supplies the hydraulic pressure for the cam rotation device and at the same time supplies the bearings of the camshaft with lubricating oil.
  • the characteristic feature of claim 1 serves to solve this problem. Since two separate drives are used to drive the two oil pumps from the crankshaft and to separate the functions, one oil pump for supplying lubricating oil, the other oil pump is used exclusively for building up the hydraulic pressure on the camshaft twisting device both oil pumps are optimally designed with regard to delivery volume and delivery pressure. While the main oil pump for supplying lubricating oil supplies relatively large amounts of oil with low pressure, the second oil pump is designed in such a way that it delivers a small amount of delivery with significantly higher pressure.
  • a space-saving design is realized in that the drives of both pumps and a camshaft drive emanating from the crankshaft are located between the flywheel and the crankshaft end bearing, so that none in the axial direction of the internal combustion engine for the drives of the oil pumps additional space is required. If the main oil pump is below the crankshaft, the second oil pump and its drive together with the camshaft drive are above the crankshaft, this space is fully used.
  • Another space advantage can be achieved in that the second oil pump is integrated in an idler gear of the camshaft drive and is driven by it lying coaxially to the idler gear.
  • a flywheel 3 On a crankshaft 2 of an 8-cylinder V-engine mounted in a crankcase 1, a flywheel 3 is screwed to the output-side end face with several screws 4.
  • a camshaft drive emanating from the crankshaft 2 is arranged between the flywheel 3 and the final bearing 5. It consists of a gear 7 of an idler gear 8 meshing with a crankshaft gear 6 and two chain drives driven by the idler gear 8 to the four camshafts 11, 12, 13, 14 assigned to the two cylinder rows 9, 10, each of which has a double sprocket 11 ', 12 ', 13', 14 'wear.
  • the double sprockets 11 ', 12' are driven by a double sprocket 16 with a double roller chain 15
  • the double sprockets 13 ', 14' are driven by a double sprocket 18 with a double roller chain 17.
  • the double sprockets 16, 18 are formed in one piece and attached to the hub sleeve 19 of the gear 7.
  • an oil pump 20 which supplies hydraulic turning devices 21, 22 on the camshafts 11, 13 with hydraulic pressure.
  • the rotational position between the camshafts 11, 13 and the chain wheels 11 ', 13' assigned to them is changed with the twisting devices.
  • a pump wheel 24 is fastened on a hollow hub 23 of the gear wheel 7.
  • the oil pump 20 is covered by a pump cover 25 which, together with a cover disk 26 screwed to it, forms the pump housing.
  • a bearing sleeve 27 is fastened in the pump cover 15, on which the intermediate wheel 8 is mounted and through which the oil supply to the oil pump 20 takes place.
  • crankshaft 2 to idler gear 8 has a ratio of 1: 2, but the sprocket ratio from idler gear 8 to camshafts 11, 12, 13, 14 is 1: 1, camshafts 11, 12, 13, 14 also run half crankshaft speed around.
  • the main oil pump 30 is driven by the crankshaft 2 with a chain drive 31. It sucks in lubricating oil from the oil pan 32 and pumps it with a pressure of approx. 3 bar to the bearing points of the internal combustion engine to be lubricated. A partial flow of this oil passes through the central bore of the bearing sleeve 27 to the oil pump 20, which increases the oil pressure to approximately 8 bar and gives it to the hydraulic camshaft twisting devices 21. Since this hydraulic pressure is very high, the camshaft rotating devices 21 can be made small-volume in the desired manner.
  • the chain drive 31 is formed by a chain wheel 33 fastened to the crankshaft 2, a chain 34 and a chain wheel 35 fastened to the main oil pump 30.
  • the chain wheel 33 is composed of two half-shells which were formed by radial blasting of a cylindrical chain wheel hub. In a groove 36 of the crankshaft 2, the two half-shells of the chain wheel 33 are joined together again at their break point and held axially.
  • a tension ring 37 mounted on the chain wheel 35 holds the two half shells together radially.
  • the sprocket 33 is locked in the circumferential direction with a fitting sleeve 38 which is fixed in the crankshaft 2 and which was pushed through during assembly through an aligned bore 39 of the flywheel.
  • the ring gear 40 of the chain wheel 33 and thus the entire chain drive 31 is located centrally between the two double chain wheels 16, 18 of the camshaft drive.
  • crankshaft gear 6 is pushed for assembly over the smoothly turned outer surface 41 of the crankshaft 2 until it rests on the clamping ring 37. At this seat it is shrunk onto the crankshaft 2.

Description

Die Erfindung betrifft eine Vorrichtung zum Antrieb zweier, an einer Hubkolben-Brennkraftmaschine angeordneter Ölpumpen nach dem Oberbegriff des Anspruchs 1, der von DE-A-26 20 480 ausgeht.The invention relates to a device for driving two oil pumps arranged on a reciprocating piston internal combustion engine according to the preamble of claim 1, which is based on DE-A-26 20 480.

Aus dieser Druckschrift ist eine Schmierölversorgung für eine Brennkraftmaschine bekannt, die eine Hauptölpumpe zur Versorgung eines Hauptschmierölkreislaufs und eine zweite Ölpumpe für einen Nebenschmierölkreislauf von Hilfsmaschinen aufweist.From this publication a lubricating oil supply for an internal combustion engine is known, which has a main oil pump for supplying a main lubricating oil circuit and a second oil pump for a secondary lubricating oil circuit of auxiliary machines.

In EP-PS 163 046 ist eine hydraulische Vorrichtung zur Winkelverstellung zweier Nockenwellen beschrieben, bei der eine Ölpumpe den Hydraulikdruck für die Nockenverdrehvorrichtung liefert und zugleich die Lager der Nockenwelle mit Schmieröl versorgt.EP-PS 163 046 describes a hydraulic device for adjusting the angle of two camshafts, in which an oil pump supplies the hydraulic pressure for the cam rotation device and at the same time supplies the bearings of the camshaft with lubricating oil.

Es ist die Aufgabe der Erfindung, zwei Ölpumpen an einer Hubkolben-Brennkraftmaschine so anzuordnen und anzutreiben, daß eine optimale Schmierung und Nockenwellenverstellung und zugleich eine kompakte, raumsparende Bauweise ermöglicht wird.It is the object of the invention to arrange and drive two oil pumps on a reciprocating piston internal combustion engine in such a way that optimum lubrication and camshaft adjustment and at the same time a compact, space-saving design is made possible.

Zur Lösung dieser Aufgabe dienen die kennzeichnenden Merkmal des Anspruchs 1. Da zum Antrieb der beiden Ölpumpen von der Kurbelwelle aus zwei getrennte Antriebe verwendet sind und zur Funktionstrennung die eine Ölpumpe zur Schmierölversorgung, die andere Ölpumpe ausschließlich zum Aufbau des Hydraulikdrucks an der Nockenwellenverdrehvorrichtung dient, lassen sich beide Ölpumpen hinsichtlich Fördervolumen und Förderdruck optimal auslegen. Während die Hauptölpumpe zur Schmierölversorgung verhältnismäßig große Ölmengen mit geringem Druck fördert, ist die zweite Ölpumpe so ausgelegt, daß sie eine geringe Fördermenge mit bedeutend höherem Druck liefert.The characteristic feature of claim 1 serves to solve this problem. Since two separate drives are used to drive the two oil pumps from the crankshaft and to separate the functions, one oil pump for supplying lubricating oil, the other oil pump is used exclusively for building up the hydraulic pressure on the camshaft twisting device both oil pumps are optimally designed with regard to delivery volume and delivery pressure. While the main oil pump for supplying lubricating oil supplies relatively large amounts of oil with low pressure, the second oil pump is designed in such a way that it delivers a small amount of delivery with significantly higher pressure.

Eine raumsparende Bauweise ist dadurch realisiert, daß die Antriebe beider Pumpen sowie ein von der Kurbelwelle ausgehender Nockenwellenantrieb zwischen dem Schwungrad und dem Endlager der Kurbelwelle liegen, so daß in axialer Richtung der Brennkraftmaschine für die Antriebe der Ölpumpen kein zusätzlicher Platz erforderlich ist. Wenn die Hauptölpumpe unterhalb der Kurbelwelle, die zweite Ölpumpe und ihr Antrieb zusammen mit dem Nockenwellenantrieb oberhalb der Kurbelwelle liegen, ist dieser Raum voll genutzt.A space-saving design is realized in that the drives of both pumps and a camshaft drive emanating from the crankshaft are located between the flywheel and the crankshaft end bearing, so that none in the axial direction of the internal combustion engine for the drives of the oil pumps additional space is required. If the main oil pump is below the crankshaft, the second oil pump and its drive together with the camshaft drive are above the crankshaft, this space is fully used.

Ein weiterer Raumvorteil läßt sich erzielen, indem nach Anspruch 3 die zweite Ölpumpe in einem Zwischenrad des Nockenwellenantriebes integriert ist und koaxial zum Zwischenrad liegend von ihm angetrieben ist.Another space advantage can be achieved in that the second oil pump is integrated in an idler gear of the camshaft drive and is driven by it lying coaxially to the idler gear.

Weitere Unteransprüche beinhalten vorteilhafte konstruktive Ausgestaltungen des erfindungsgemäßen Ölpumpenantriebes.Further subclaims contain advantageous structural designs of the oil pump drive according to the invention.

Ein Ausführungsbeispiel der Erfindung ist in der Zeichnung dargestellt und wird nachfolgend erläutert. Es zeigt:

Fig. 1
Querschnitt einer Hubkolben-Brennkraftmaschine mit Nockenwellenantrieb,
Fig. 2
Ölpumpenantrieb einer Hubkolben-Brennkraftmaschine nach Fig. 1,
Fig. 3
längsschnitt durch den Nockenwellen- und Ölpumpenantrieb nach Fig. 1 und Fig. 2.
An embodiment of the invention is shown in the drawing and is explained below. It shows:
Fig. 1
Cross section of a reciprocating piston internal combustion engine with camshaft drive,
Fig. 2
Oil pump drive of a reciprocating piston internal combustion engine according to FIG. 1,
Fig. 3
longitudinal section through the camshaft and oil pump drive according to FIGS. 1 and 2.

An einer in einem Kurbelgehäuse 1 gelagerten Kurbelwelle 2 eines 8-Zylinder-V-Motors ist an die abtriebsseitige Stirnfläche ein Schwungrad 3 mit mehreren Schrauben 4 angeschraubt. Zwischen dem Schwungrad 3 und dem Endlager 5 ist ein von der Kurbelwelle 2 ausgehender Nockenwellenantrieb angeordnet. Er besteht aus einem mit einem Kurbelwellenzahnrad 6 kämmenden Zahnrad 7 eines Zwischenrads 8 und zwei von dem Zwischenrad 8 angetriebenen Kettentrieben zu den vier, den beiden Zylinderreihen 9, 10 zugeordneten Nockenwellen 11, 12, 13, 14, die jeweils ein Doppelkettenrad 11', 12', 13', 14' tragen. Die Doppelkettenräder 11', 12' werden mit einer Doppelrollenkette 15 von einem Doppelkettenrad 16, die Doppelkettenräder 13', 14' mit einer Doppelrollenkette 17 von einem Doppelkettenrad 18 angetrieben. Die Doppelkettenräder 16, 18 sind einstückig ausgebildet und auf der Nabenhülse 19 des Zahnrads 7 befestigt.On a crankshaft 2 of an 8-cylinder V-engine mounted in a crankcase 1, a flywheel 3 is screwed to the output-side end face with several screws 4. A camshaft drive emanating from the crankshaft 2 is arranged between the flywheel 3 and the final bearing 5. It consists of a gear 7 of an idler gear 8 meshing with a crankshaft gear 6 and two chain drives driven by the idler gear 8 to the four camshafts 11, 12, 13, 14 assigned to the two cylinder rows 9, 10, each of which has a double sprocket 11 ', 12 ', 13', 14 'wear. The double sprockets 11 ', 12' are driven by a double sprocket 16 with a double roller chain 15, the double sprockets 13 ', 14' are driven by a double sprocket 18 with a double roller chain 17. The double sprockets 16, 18 are formed in one piece and attached to the hub sleeve 19 of the gear 7.

An der anderen Stirnseite des Zahnrades 7 ist eine Ölpumpe 20 angeordnet, die hydraulische Verdrehvorrichtungen 21, 22 an den Nockenwellen 11, 13 mit Hydraulikdruck versorgt. Mit den Verdrehvorrichtungen wird die Drehlage zwischen den Nockenwellen 11, 13 und den ihnen zugeordneten Kettenräder 11', 13' geändert. Auf einer Hohlnabe 23 des Zahnrades 7 ist ein Pumpenrad 24 befestigt. Die Ölpumpe 20 ist durch einen Pumpendeckel 25 abgedeckt, der zusammen mit einer an ihm festgeschraubten Deckscheibe 26 das Pumpengehäuse bildet. Im Pumpendeckel 15 ist eine Lagerhülse 27 befestigt, auf der das Zwischenrad 8 gelagert ist und durch die hindurch die Ölzufuhr zur Ölpumpe 20 erfolgt.On the other end of the gear 7, an oil pump 20 is arranged, which supplies hydraulic turning devices 21, 22 on the camshafts 11, 13 with hydraulic pressure. The rotational position between the camshafts 11, 13 and the chain wheels 11 ', 13' assigned to them is changed with the twisting devices. A pump wheel 24 is fastened on a hollow hub 23 of the gear wheel 7. The oil pump 20 is covered by a pump cover 25 which, together with a cover disk 26 screwed to it, forms the pump housing. A bearing sleeve 27 is fastened in the pump cover 15, on which the intermediate wheel 8 is mounted and through which the oil supply to the oil pump 20 takes place.

Da die Zahnradübersetzung von der Kurbelwelle 2 zum Zwischenrad 8 ein Verhältnis von 1:2 hat, die Kettenradübersetzung vom Zwischenrad 8 zu den Nokkenwellen 11, 12, 13, 14 aber 1:1 ist, laufen die Nockenwellen 11, 12, 13, 14 mit halber Kurbelwellendrehzahl um.Since the gear ratio from crankshaft 2 to idler gear 8 has a ratio of 1: 2, but the sprocket ratio from idler gear 8 to camshafts 11, 12, 13, 14 is 1: 1, camshafts 11, 12, 13, 14 also run half crankshaft speed around.

Die Hauptölpumpe 30 wird von der Kurbelwelle 2 mit einem Kettentrieb 31 angetrieben . Sie saugt Schmieröl aus der Ölwanne 32 an und pumpt es mit einem Druck von ca. 3 bar zu den zu schmierenden Lagerstellen der Brennkraftmaschine. Ein Teilstrom diese Öls gelangt über die Zentralbohrung der Lagerhülse 27 zu der Ölpumpe 20, die den Öldruck auf ca. 8 bar erhöht und auf die hydraulischen Nockenwellenverdrehvorrichtungen 21 gibt. Da dieser Hydraulikdruck sehr hoch ist, können die Nockenwellenverdrehvorrichtungen 21 in erwünschter Weise kleinvolumig ausgeführt werden.The main oil pump 30 is driven by the crankshaft 2 with a chain drive 31. It sucks in lubricating oil from the oil pan 32 and pumps it with a pressure of approx. 3 bar to the bearing points of the internal combustion engine to be lubricated. A partial flow of this oil passes through the central bore of the bearing sleeve 27 to the oil pump 20, which increases the oil pressure to approximately 8 bar and gives it to the hydraulic camshaft twisting devices 21. Since this hydraulic pressure is very high, the camshaft rotating devices 21 can be made small-volume in the desired manner.

Der Kettentrieb 31 wird gebildet durch ein auf der Kurbelwelle 2 befestigtes Kettenrad 33, eine Kette 34 und ein an der Hauptölpumpe 30 befestigtes Kettenrad 35. Das Kettenrad 33 ist aus zwei Halbschalen zusammengesetzt, die durch radiales Sprengen einer zylindrischen Kettenradnabe gebildet wurden. In einer Nut 36 der Kurbelwelle 2 sind die beiden Halbschalen des Kettenrades 33 an ihrer Bruchstelle wieder zusammengefügt und axial gehalten. Ein auf das Kettenrad 35 aufgezogener Spannring 37 hält die beiden Halbschalen radial zusammen. Mit einer in der Kurbelwelle 2 festen Paßhülse 38, die bei Montage durch eine zu ihr fluchtende Bohrung 39 des Schwungrades durchgesteckt wurde, wird das Kettenrad 33 in Umfangsrichtung arretiert. Der Zahnkranz 40 des Kettenrades 33 und somit der gesamte Kettentrieb 31 liegt mittig zwischen den beiden Doppelkettenrädern 16, 18 des Nockenwellenantriebs.The chain drive 31 is formed by a chain wheel 33 fastened to the crankshaft 2, a chain 34 and a chain wheel 35 fastened to the main oil pump 30. The chain wheel 33 is composed of two half-shells which were formed by radial blasting of a cylindrical chain wheel hub. In a groove 36 of the crankshaft 2, the two half-shells of the chain wheel 33 are joined together again at their break point and held axially. A tension ring 37 mounted on the chain wheel 35 holds the two half shells together radially. The sprocket 33 is locked in the circumferential direction with a fitting sleeve 38 which is fixed in the crankshaft 2 and which was pushed through during assembly through an aligned bore 39 of the flywheel. The ring gear 40 of the chain wheel 33 and thus the entire chain drive 31 is located centrally between the two double chain wheels 16, 18 of the camshaft drive.

Das Kurbelwellenzahnrad 6 wird zur Montage über die glatt abgedrehte Mantelfläche 41 der Kurbelwelle 2 geschoben, bis es an dem Spannring 37 anliegt. An dieser Sitzstelle wird es auf die Kurbelwelle 2 aufgeschrumpft.The crankshaft gear 6 is pushed for assembly over the smoothly turned outer surface 41 of the crankshaft 2 until it rests on the clamping ring 37. At this seat it is shrunk onto the crankshaft 2.

Claims (7)

  1. A device for driving two oil pumps arranged on a reciprocating piston internal-combustion engine, having a main oil pump (30) for providing the circulation of lubricating oil in the internal-combustion engine and a second oil pump (20), wherein the valves of the internal-combustion engine are operated by camshafts (11, 12, 13, 14) driven by a crankshaft, characterised in that the second oil pump only supplies hydraulic pressure to a hydraulic camshaft rotating device (21), in that the main oil pump (30) and the second oil pump (20) are driven via separate drives (chain drive 31; gearwheel drive 6, 7) by the crankshaft (2) mounted on the crankcase (1), and in that the drives (31) and (6, 7) and a camshaft drive issuing from the crankshaft (2) are located between a flywheel (3) secured to the drive end of the crankshaft (2) and the end bearing (5) of the crankshaft (2).
  2. A device according to claim 1, characterised in that a chain drive (31) serves to drive the main oil pump (30) and a gearwheel drive (6, 7) serves to drive the second oil pump (20).
  3. A device according to claims 1 and 2, characterised in that the second oil pump (20) is coaxially arranged on an intermediate wheel (8) and is driven thereby, the camshafts (11, 12, 13, 14) being driven by the crankshaft (2) via the intermediate wheel (8).
  4. A device according to claims 1 and 3, characterised in that a chainwheel (33) driving the main oil pump (30) is formed of two shells, held together radially by a clamping ring (37), held axially in a groove (36) of the crankshaft (2) and fixed in the circumferential direction by a fitted sleeve (38) of the crankshaft (2).
  5. A device according to claims 1 and 3, characterised in that the crankshaft gearwheel (6) meshing with the gearwheel (7) of the intermediate wheel (8), when being mounted on the crankshaft (2), can be pushed over the smoothly machined circumferential surface (41 ) of the latter until it abuts against a clamping ring (37) which radially holds together the chainwheel (33), and in that the crankshaft gearwheel (6) is shrunk onto the crankshaft (2) in this position.
  6. A device according to claim 5, characterised in that the fitted sleeve (38) can be guided through a front bore (39) of the crankshaft (2) for the purposes of assembly.
  7. A device according to claims 1 and 3, characterised in that the intermediate wheel (8) with the oil pump (20) is mounted on a bearing sleeve (27) secured in a pump cover (25), part of the lubricating oil supplied by the main oil pump (30) being fed to the oil pump (20) via the central bore of the said bearing sleeve (27).
EP90106688A 1989-07-01 1990-04-06 Driving system for two oil pumps of an internal combustion engine with reciprocating pistons Expired - Lifetime EP0406527B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3921715A DE3921715A1 (en) 1989-07-01 1989-07-01 DEVICE FOR DRIVING TWO OIL PUMPS ON A PISTON PISTON INTERNAL COMBUSTION ENGINE
DE3921715 1989-07-01

Publications (2)

Publication Number Publication Date
EP0406527A1 EP0406527A1 (en) 1991-01-09
EP0406527B1 true EP0406527B1 (en) 1993-09-08

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP90106688A Expired - Lifetime EP0406527B1 (en) 1989-07-01 1990-04-06 Driving system for two oil pumps of an internal combustion engine with reciprocating pistons

Country Status (5)

Country Link
US (1) US5063895A (en)
EP (1) EP0406527B1 (en)
JP (1) JP2888934B2 (en)
DE (2) DE3921715A1 (en)
ES (1) ES2044291T3 (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008036787A1 (en) * 2008-08-07 2010-02-11 Volkswagen Ag Reciprocating piston internal combustion engine i.e. diesel internal combustion engine, for use in motor vehicle, has drive wheel arrangements for driving cam shafts and drive wheel for driving pump

Families Citing this family (35)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3929621A1 (en) * 1989-09-06 1991-03-07 Bayerische Motoren Werke Ag DEVICE FOR RELATIVELY ADJUSTING A SHAFT TO A DRIVE WHEEL, IN PARTICULAR CAMSHAFT OF AN INTERNAL COMBUSTION ENGINE
KR950003163B1 (en) * 1990-10-31 1995-04-01 스즈끼 가부시끼가이샤 Attaching structure for oil pump of engine
DE59106923D1 (en) * 1991-01-26 1995-12-21 Porsche Ag CAMSHAFT DRIVE FOR A V-COMBUSTION ENGINE.
US5509383A (en) * 1991-02-20 1996-04-23 Itt Automotive Europe Gmbh Hydraulic unit
JPH04111505U (en) * 1991-03-15 1992-09-28 本田技研工業株式会社 Refueling system in internal combustion engines
US5184578A (en) * 1992-03-05 1993-02-09 Borg-Warner Automotive Transmission & Engine Components Corporation VCT system having robust closed loop control employing dual loop approach having hydraulic pilot stage with a PWM solenoid
GB2303669B (en) * 1995-07-20 1998-03-04 Suzuki Motor Co Oil pump sprocket cover for an internal combustion engine
DE19622676C2 (en) * 1996-06-05 1998-11-19 Daimler Benz Ag Chain drive, in particular power take-off in an internal combustion engine
DE19622688A1 (en) * 1996-06-05 1997-12-11 Bayerische Motoren Werke Ag Internal combustion engine with separate hydraulic circuits supplied with lubricating oil
DE19647299C1 (en) * 1996-11-15 1998-04-09 Daimler Benz Ag Control housing for an internal combustion engine
US5894830A (en) * 1997-12-15 1999-04-20 Caterpillar Inc. Engine having a high pressure hydraulic system and low pressure lubricating system
DE19840659A1 (en) * 1998-09-05 2000-03-09 Volkswagen Ag Control drive for camshaft arrangements
US6289878B1 (en) 1999-07-15 2001-09-18 Caterpillar Inc. Engine having multiple pumps driven by a single shaft
DE19959594C1 (en) 1999-12-10 2001-06-21 Bayerische Motoren Werke Ag Chain drive of a V-engine with overhead camshafts
JP2001342812A (en) * 2000-05-31 2001-12-14 Sanshin Ind Co Ltd Four cycle engine for outboard motor
US7674095B2 (en) * 2000-12-12 2010-03-09 Borgwarner Inc. Variable displacement vane pump with variable target regulator
US6896489B2 (en) * 2000-12-12 2005-05-24 Borgwarner Inc. Variable displacement vane pump with variable target regulator
EP1350930B2 (en) * 2002-04-03 2016-01-27 SLW Automotive Inc. Variable displacement pump and control therefor
US7726948B2 (en) * 2002-04-03 2010-06-01 Slw Automotive Inc. Hydraulic pump with variable flow and variable pressure and electric control
DE10308760B4 (en) * 2003-02-28 2005-06-30 Dr.Ing.H.C. F. Porsche Ag Timing drive for an installable in a motor vehicle internal combustion engine
US7114482B2 (en) * 2003-03-28 2006-10-03 Caterpillar Inc. Engine lubrication circuit including two pumps
US7682136B2 (en) * 2003-03-28 2010-03-23 Caterpillar Inc. Multiple pump housing
US7055486B2 (en) * 2003-03-28 2006-06-06 Caterpillar Inc. Fluid delivery control system
DE10314969A1 (en) * 2003-04-02 2004-10-14 Daimlerchrysler Ag Drive device on an internal combustion engine
US6786188B1 (en) * 2003-05-15 2004-09-07 Kawasaki Jukogyo Kabushiki Kaisha Dry-sump lubrication type four-stroke cycle engine
US7007654B2 (en) * 2003-08-04 2006-03-07 Bulent Aliev Pre-and post-ignition auxiliary oil circulation system for an internal combustion engine
US7156060B2 (en) * 2004-12-28 2007-01-02 Honda Motor Co., Ltd. Cam drive gear and valve operating system drive gear for engine
FR2882786B1 (en) * 2005-03-01 2007-04-20 Renault Sas INTERNAL COMBUSTION ENGINE HAVING A PINION ARRANGEMENT ON ONE END OF THE CRANKSHAFT
JP2007309234A (en) * 2006-05-19 2007-11-29 Honda Motor Co Ltd Lubricating device for internal combustion engine
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
CN102121520A (en) * 2010-12-27 2011-07-13 中国北车集团大连机车车辆有限公司 Gear transmission device
DE102015005344A1 (en) * 2015-04-28 2016-11-03 Volkswagen Aktiengesellschaft Accessory drive device
US10422253B2 (en) * 2016-04-26 2019-09-24 Ford Global Technologies, Llc Cam drive system for an engine
GB2551602B (en) * 2016-06-20 2020-10-28 Ford Global Tech Llc An engine assembly with improved oil pressure regulation
FR3073594B1 (en) * 2017-11-16 2021-04-30 Renault Sas ASSEMBLY FOR INTERNAL COMBUSTION ENGINES, IN PARTICULAR MOTOR VEHICLES, INCLUDING AT LEAST ONE CAMSHAFT, ONE CRANKSHAFT AND ONE TRANSMISSION

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3159047A (en) * 1962-09-21 1964-12-01 George F Dable Segmented gear
DE2620480C2 (en) * 1976-05-08 1984-03-01 Mtu Motoren- Und Turbinen-Union Friedrichshafen Gmbh, 7990 Friedrichshafen Lubricating oil supply
US4589382A (en) * 1982-01-08 1986-05-20 Honda Giken Kogyo Kabushiki Kaisha V-type multicylinder internal combustion engine
DE3415861A1 (en) * 1984-04-28 1985-10-31 Pierburg Gmbh & Co Kg, 4040 Neuss DEVICE FOR CONTROLLING A COUPLING DEVICE
DE3619577A1 (en) * 1986-06-11 1987-12-17 Kloeckner Humboldt Deutz Ag Belt or chain drive of an internal combustion engine with oil pump drive as idler pulley
IT208998Z2 (en) * 1986-12-23 1988-09-02 Fiat Auto Spa CONTROL DEVICE FOR AN OIL PUMP IN AN INTERNAL COMBUSTION ENGINE
US4878461A (en) * 1987-02-24 1989-11-07 Siemens-Bendix Automotive Electronics L.P. Variable camshaft timing system
DE3729603A1 (en) * 1987-09-04 1989-03-16 Porsche Ag LUBRICATION DEVICE FOR A PISTON PISTON ENGINE

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008036787A1 (en) * 2008-08-07 2010-02-11 Volkswagen Ag Reciprocating piston internal combustion engine i.e. diesel internal combustion engine, for use in motor vehicle, has drive wheel arrangements for driving cam shafts and drive wheel for driving pump

Also Published As

Publication number Publication date
JP2888934B2 (en) 1999-05-10
DE3921715A1 (en) 1991-01-10
ES2044291T3 (en) 1994-01-01
JPH0343613A (en) 1991-02-25
US5063895A (en) 1991-11-12
EP0406527A1 (en) 1991-01-09
DE59002620D1 (en) 1993-10-14

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