EP0406527A1 - 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

Info

Publication number
EP0406527A1
EP0406527A1 EP90106688A EP90106688A EP0406527A1 EP 0406527 A1 EP0406527 A1 EP 0406527A1 EP 90106688 A EP90106688 A EP 90106688A EP 90106688 A EP90106688 A EP 90106688A EP 0406527 A1 EP0406527 A1 EP 0406527A1
Authority
EP
European Patent Office
Prior art keywords
crankshaft
oil pump
gear
driven
internal combustion
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.)
Granted
Application number
EP90106688A
Other languages
German (de)
French (fr)
Other versions
EP0406527B1 (en
Inventor
Herbert Dipl.-Ing. Ampferer (Fh)
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Dr Ing HCF Porsche AG
Original Assignee
Dr Ing HCF Porsche AG
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Dr Ing HCF Porsche AG filed Critical Dr Ing HCF Porsche AG
Publication of EP0406527A1 publication Critical patent/EP0406527A1/en
Application granted granted Critical
Publication of EP0406527B1 publication Critical patent/EP0406527B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

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.
  • 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 achieved in that the drives of both pumps are located at the point of the crankshaft from which the camshaft drive also takes place, so that no additional space is required in the axial direction of the internal combustion engine for the drives of the oil pumps. If the main oil pump is below the crankshaft, the second oil pump and its drive this space is fully used together with the camshaft drive above the crankshaft.
  • a further space advantage can be achieved by the second oil pump being integrated in an idler gear of the camshaft drive and being 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 meshing with a crankshaft gear 6 gear 7 of an idler gear 8 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 with a double roller chain 15 by a double sprocket 16, the double sprockets 13 ', 14' with a double roller chain 17 by a double sprocket 18.
  • 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. With the twisting devices, the rotational position between the camshafts 11, 13 and their associated sprockets 11 ', 13' is changed.
  • 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.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Lubrication Of Internal Combustion Engines (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)
  • Valve Device For Special Equipments (AREA)
  • Reciprocating Pumps (AREA)

Abstract

Der Schmierölkreislauf einer Hubkolben-Brennkraftmaschine wird durch eine in der Ölwanne angeordnete, von der Kurbelwelle (2) angetriebene Hauptölpumpe (30) versorgt. Eine zweite, ebenfalls von der Kurbelwelle angetriebene Ölpumpe (20), liefert Hydraulikdruck an hydraulische Nockenwellenverdrehvorrichtungen. Die zweite Ölpumpe (20) ist in einem Zwischenrad (7) integriert und von ihm angetrieben, über das die Nockenwellen von der Kurbelwelle angetrieben sind.The lubricating oil circuit of a reciprocating piston internal combustion engine is supplied by a main oil pump (30) arranged in the oil pan and driven by the crankshaft (2). A second oil pump (20), also driven by the crankshaft, supplies hydraulic pressure to hydraulic camshaft turning devices. The second oil pump (20) is integrated in an intermediate wheel (7) and driven by it, via which the camshafts are driven by the crankshaft.

Description

Die Erfindung betrifft eine Vorrichtung zum Antrieb zweier, an einer Hubkolben-Brennkraftmaschine angeordneter Ölpumpen nach dem Oberbegriff des Anspruchs 1.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.

Aus DE-OS 26 20 480 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 DE-OS 26 20 480 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 an der Stelle der Kurbelwelle liegen, von der aus auch der Nockenwel­lenantrieb erfolgt, 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 achieved in that the drives of both pumps are located at the point of the crankshaft from which the camshaft drive also takes place, so that no additional space is required in the axial direction of the internal combustion engine for the drives of the oil pumps. If the main oil pump is below the crankshaft, the second oil pump and its drive this space is fully used together with the camshaft drive above the crankshaft.

Ein weiterer Raumvorteil läßt sich erzielen, indem nach Anspruch 5 die zweite Ölpumpe in einem Zwischenrad des Nockenwellenantriebes integriert ist und koaxial zum Zwischenrad liegend von ihm angetrieben ist.A further space advantage can be achieved by the second oil pump being integrated in an idler gear of the camshaft drive and being driven by it lying coaxially to the idler gear.

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

Ein Ausführungsbeispiel der Erfindung ist in der Zeichnung dargestellt und wird nachfolgend erläutert.An embodiment of the invention is shown in the drawing and is explained below.

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.
It shows:
  • 1 cross section of a reciprocating piston internal combustion engine with camshaft drive,
  • 2 oil pump drive of a reciprocating piston internal combustion engine according to FIG. 1,
  • 3 shows a 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 meshing with a crankshaft gear 6 gear 7 of an idler gear 8 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 with a double roller chain 15 by a double sprocket 16, the double sprockets 13 ', 14' with a double roller chain 17 by a double sprocket 18. 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. With the twisting devices, the rotational position between the camshafts 11, 13 and their associated sprockets 11 ', 13' is changed. 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 (8)

1. Vorrichtung zum Antrieb zweier, an einer Hubkolben-Brennkraftmaschine an­geordneter Ölpumpen, mit einer Hauptölpumpe zur Versorgung des Schmieröl­kreislaufs der Brennkraftmaschine und einer zweiten Ölpumpe, wobei die Ventile der Brennkraftmaschine durch Nockenwellen betätigt sind, die von einer Kurbelwelle getrieben sind, dadurch gekennzeichnet, daß die zweite Ölpumpe lediglich Hydraulikdruck an eine hydraulische Nockenwellenverdrehvorrichtung (21) liefert, daß die Hauptölpumpe (30) und die zweite Ölpumpe (20) mit getrennten Antrieben (Kettentrieb 31; Zahnrad­trieb 6, 7) von der am Kurbelgehäuse (1) gelagerten Kurbelwelle (2) angetrieben sind, und daß die Antriebe (31) und (6, 7) an der selben Stelle der Kurbelwelle (2) liegen, wie ein von der Kurbelwelle (2) ausgehender Nockenwellenantrieb.1.Device for driving two oil pumps arranged on a reciprocating piston internal combustion engine, with a main oil pump for supplying the lubricating oil circuit of the internal combustion engine and a second oil pump, the valves of the internal combustion engine being actuated by camshafts which are driven by a crankshaft, characterized in that the second oil pump only supplies hydraulic pressure to a hydraulic camshaft turning device (21) that the main oil pump (30) and the second oil pump (20) with separate drives (chain drive 31; gear drive 6, 7) from the crankshaft (2) mounted on the crankcase (1) ) are driven, and that the drives (31) and (6, 7) are located at the same point on the crankshaft (2) as a camshaft drive originating from the crankshaft (2). 2. Vorrichtung nach Anspruch 1, dadurch gekennzeichnet, daß die Antriebe (31) und (6, 7) zwischen einem am abtriebsseitigen Ende der Kurbelwelle (2) befe­stigten Schwungrad (3) und dem Endlager (5) der Kurbelwelle (2) liegen.2. Device according to claim 1, characterized in that the drives (31) and (6, 7) lie between a flywheel (3) attached to the output-side end of the crankshaft (2) and the end bearing (5) of the crankshaft (2). 3. Vorrichtung nach Anspruch 1, dadurch gekennzeichnet, daß zum Antrieb der Hauptölpumpe (30) ein Kettentrieb (31), zum Antrieb der zweiten Ölpumpe (20) ein Zahnradtrieb (6, 7) dient.3. Apparatus according to claim 1, characterized in that a chain drive (31), for driving the main oil pump (30), a gear drive (6, 7) is used to drive the second oil pump (20). 4. Vorrichtung nach Anspruch 1 und 3, dadurch gekennzeichnet, daß die zweite Ölpumpe (20) an einem Zwischenrad (8) koaxial angeordnet und von ihm ange­trieben ist, über das die Nockenwellen (11, 12, 13, 14) von der Kurbelwelle (2) angetrieben sind.4. Apparatus according to claim 1 and 3, characterized in that the second oil pump (20) on an intermediate wheel (8) is arranged coaxially and driven by it, via which the camshafts (11, 12, 13, 14) from the crankshaft ( 2) are driven. 5. Vorrichtung nach Anspruch 1 und 4, dadurch gekennzeichnet, daß das die Hauptölpumpe (30) antreibende Kettenrad (33) zweischalig ausgebildet, durch einen Spannring (37) radial zusammengehalten, axial in einer Nut (36) der Kurbelwelle (2) gehalten und in Umfangsrichtung durch eine Paßhülse (38) der Kurbelwelle (2) fixiert ist.5. Apparatus according to claim 1 and 4, characterized in that the main oil pump (30) driving sprocket (33) is formed in two shells, held together radially by a clamping ring (37), held axially in a groove (36) of the crankshaft (2) and is fixed in the circumferential direction by an adapter sleeve (38) of the crankshaft (2). 6) Vorrichtung nach Anspruch 2 und 4, dadurch gekennzeichnet, daß das mit dem Zahnrad (7) des Zwischenrads (8) kämmende Kurbelwellenzahnrad (6) bei der Montage auf der Kurbelwelle (2) über deren glatt abgedrehte Mantelfläche (41) bis zur Anlage an einem Spannring (37) aufschiebbar ist, der das Kettenrad (33) radial zusammenhält und daß das Kurbelwellenzahnrad (6) an dieser Sitzstelle auf die Kurbelwelle (2) aufgeschrumpft ist.6) Device according to claim 2 and 4, characterized in that the meshing with the gear (7) of the intermediate gear (8) crankshaft gear (6) during assembly on the crankshaft (2) via its smoothly turned outer surface (41) to the system can be pushed onto a clamping ring (37) which holds the chain wheel (33) together radially and that the crankshaft gear (6) is shrunk onto the crankshaft (2) at this seat. 7. Vorrichtung nach Anspruch 6, dadurch gekennzeichnet, daß die Paßhülse (38) zur Montage durch eine stirnseitige Bohrung (39) der Kurbelwelle (2) hin­durchführbar ist.7. The device according to claim 6, characterized in that the fitting sleeve (38) for mounting through an end bore (39) of the crankshaft (2) can be passed. 8. Vorrichtung nach Anspruch 1 und 4, dadurch gekennzeichnet, daß das Zwi­schenrad (8) samt Ölpumpe (20) auf einer in einem Pumpendeckel (25) befe­stigten Lagerhülse (27) gelagert ist, über deren Zentralbohrung der Ölpumpe (20) ein Teil des von der Hauptölpumpe (30) geförderten Schmieröls zugeführt wird.8. Apparatus according to claim 1 and 4, characterized in that the intermediate wheel (8) together with the oil pump (20) on a in a pump cover (25) fixed bearing sleeve (27) is mounted, via the central bore of the oil pump (20) a part of from the main oil pump (30) delivered lubricating oil.
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
DE3921715 1989-07-01
DE3921715A DE3921715A1 (en) 1989-07-01 1989-07-01 DEVICE FOR DRIVING TWO OIL PUMPS ON A PISTON PISTON INTERNAL COMBUSTION ENGINE

Publications (2)

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

Family

ID=6384126

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 (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1992013177A1 (en) * 1991-01-26 1992-08-06 Dr.Ing.H.C. F. Porsche Aktiengesellschaft Camshaft drive unit for a v-type internal-combustion engine
WO1992014641A1 (en) * 1991-02-20 1992-09-03 Alfred Teves Gmbh Hydraulic system
EP0503635A1 (en) * 1991-03-15 1992-09-16 Honda Giken Kogyo Kabushiki Kaisha Oil supply system in internal combustion engine
US5190005A (en) * 1990-10-31 1993-03-02 Suzuki Motor Corporation Attaching structure for oil pump of engine
DE19622688A1 (en) * 1996-06-05 1997-12-11 Bayerische Motoren Werke Ag Internal combustion engine with separate hydraulic circuits supplied with lubricating oil
FR3073594A1 (en) * 2017-11-16 2019-05-17 Renault S.A.S. ASSEMBLY FOR AN INTERNAL COMBUSTION ENGINE, IN PARTICULAR A MOTOR VEHICLE, COMPRISING AT LEAST ONE CAMSHAFT, A CRANKSHAFT AND A TRANSMISSION DEVICE

Families Citing this family (30)

* 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
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
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
US7726948B2 (en) * 2002-04-03 2010-06-01 Slw Automotive Inc. Hydraulic pump with variable flow and variable pressure and electric control
EP1350930B2 (en) * 2002-04-03 2016-01-27 SLW Automotive Inc. Variable displacement pump and control therefor
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
US7682136B2 (en) * 2003-03-28 2010-03-23 Caterpillar Inc. Multiple pump housing
US7114482B2 (en) * 2003-03-28 2006-10-03 Caterpillar Inc. Engine lubrication circuit including two pumps
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
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
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

Citations (5)

* 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
DE2620480A1 (en) * 1976-05-08 1977-11-24 Motoren Turbinen Union Dry sump IC engine lubricant supply system - has cooled oil feed from main cycle to separate cycle for auxiliaries
EP0163046A1 (en) * 1984-04-28 1985-12-04 Pierburg Gmbh Device for adjusting the angle of a shaft, especially of a camshaft relative to a drive shaft
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
EP0272677A1 (en) * 1986-12-23 1988-06-29 FIAT AUTO S.p.A. Internal combustion engine

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4589382A (en) * 1982-01-08 1986-05-20 Honda Giken Kogyo Kabushiki Kaisha V-type multicylinder 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

Patent Citations (5)

* 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
DE2620480A1 (en) * 1976-05-08 1977-11-24 Motoren Turbinen Union Dry sump IC engine lubricant supply system - has cooled oil feed from main cycle to separate cycle for auxiliaries
EP0163046A1 (en) * 1984-04-28 1985-12-04 Pierburg Gmbh Device for adjusting the angle of a shaft, especially of a camshaft relative to a drive shaft
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
EP0272677A1 (en) * 1986-12-23 1988-06-29 FIAT AUTO S.p.A. Internal combustion engine

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5190005A (en) * 1990-10-31 1993-03-02 Suzuki Motor Corporation Attaching structure for oil pump of engine
GB2249346B (en) * 1990-10-31 1995-05-24 Suzuki Motor Co Attaching structure of oil pump of engine
WO1992013177A1 (en) * 1991-01-26 1992-08-06 Dr.Ing.H.C. F. Porsche Aktiengesellschaft Camshaft drive unit for a v-type internal-combustion engine
US5386808A (en) * 1991-01-26 1995-02-07 Dr. Ing, H.C.F. Porsche Ag Camshaft drive for an internal-combustion V-engine
WO1992014641A1 (en) * 1991-02-20 1992-09-03 Alfred Teves Gmbh Hydraulic system
US5509383A (en) * 1991-02-20 1996-04-23 Itt Automotive Europe Gmbh Hydraulic unit
EP0503635A1 (en) * 1991-03-15 1992-09-16 Honda Giken Kogyo Kabushiki Kaisha Oil supply system in internal combustion engine
US5195474A (en) * 1991-03-15 1993-03-23 Honda Giken Kogyo Kabushiki Kaisha Oil supply system in internal conbustion engine
DE19622688A1 (en) * 1996-06-05 1997-12-11 Bayerische Motoren Werke Ag Internal combustion engine with separate hydraulic circuits supplied with lubricating oil
FR3073594A1 (en) * 2017-11-16 2019-05-17 Renault S.A.S. ASSEMBLY FOR AN INTERNAL COMBUSTION ENGINE, IN PARTICULAR A MOTOR VEHICLE, COMPRISING AT LEAST ONE CAMSHAFT, A CRANKSHAFT AND A TRANSMISSION DEVICE
EP3486524A1 (en) * 2017-11-16 2019-05-22 RENAULT s.a.s. Assembly for internal combustion engine, in particular of a motor vehicle, comprising at least one camshaft, a crankshaft and a transmission member

Also Published As

Publication number Publication date
EP0406527B1 (en) 1993-09-08
US5063895A (en) 1991-11-12
DE3921715A1 (en) 1991-01-10
DE59002620D1 (en) 1993-10-14
JP2888934B2 (en) 1999-05-10
ES2044291T3 (en) 1994-01-01
JPH0343613A (en) 1991-02-25

Similar Documents

Publication Publication Date Title
EP0406527B1 (en) Driving system for two oil pumps of an internal combustion engine with reciprocating pistons
EP0599125B1 (en) Driving arrangement for the balancing shaft of a V-type engine
DE4024057C1 (en)
EP0406528B1 (en) Camshaft drive for multicylinder v-engine
DE3641201C2 (en)
EP1257741B1 (en) Starting device for a twin cylinder internal combustion engine in a v-format
EP0469334B1 (en) Method for changing the angular position of shafts for an internal combustion engine
DE3226458A1 (en) MOTOR VEHICLE ENGINE
DE3541065A1 (en) GEAR ASSEMBLY FOR TRANSMITTING THE ROTATION BETWEEN TWO SHAFTS
EP0809041A2 (en) Means for equilibration of inertial torque in internal combustion engines
AT389739B (en) FOUR-STROKE COMBUSTION ENGINE WITH A LUBRICATED OIL PUMP DESIGNED AS A GEAR PUMP
DE19535963B4 (en) System for taking power from a crankshaft
DE4304743C2 (en) Drive unit for a motor vehicle
EP0624717B1 (en) Internal combustion engine with an adjuster unit to vary the phase of the camshafts drive
DE102018000533A1 (en) rotary pump
DE19837091C2 (en) Device for balancing free mass forces of an internal combustion engine
DE4242871A1 (en) Gear-type engine oil pump
DE2823992A1 (en) PISTON COMPRESSOR ATTACHED AS AUXILIARY MACHINE
DE3809566C2 (en)
EP0255705B1 (en) Internal combustion engine
EP0568527A1 (en) Camshaft drive unit for a v-type internal-combustion engine.
DE4037272A1 (en) Reciprocating piston IC engine - has two crankshafts, and extra space for accessory drives
DE10012892B4 (en) Oil pump drive for an internal combustion engine
DE4104219A1 (en) Drive device for IC engine with two camshafts - has independent camshaft drives off chain and sprocket
DE3010756A1 (en) HYDRAULIC PUMP DRIVE DEVICE

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): DE ES FR GB IT NL SE

17P Request for examination filed

Effective date: 19910413

17Q First examination report despatched

Effective date: 19920629

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE ES FR GB IT NL SE

REF Corresponds to:

Ref document number: 59002620

Country of ref document: DE

Date of ref document: 19931014

ITF It: translation for a ep patent filed

Owner name: ING. C. GREGORJ S.P.A.

GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)

Effective date: 19930921

ET Fr: translation filed
REG Reference to a national code

Ref country code: ES

Ref legal event code: FG2A

Ref document number: 2044291

Country of ref document: ES

Kind code of ref document: T3

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 19940328

Year of fee payment: 5

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SE

Effective date: 19940407

Ref country code: ES

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 19940407

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed
PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: NL

Effective date: 19941101

NLV4 Nl: lapsed or anulled due to non-payment of the annual fee
EUG Se: european patent has lapsed

Ref document number: 90106688.6

Effective date: 19941110

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 19950413

Year of fee payment: 6

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Effective date: 19951229

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Effective date: 19960406

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 19960406

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 19970515

Year of fee payment: 8

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 19990202

REG Reference to a national code

Ref country code: ES

Ref legal event code: FD2A

Effective date: 19990301

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES;WARNING: LAPSES OF ITALIAN PATENTS WITH EFFECTIVE DATE BEFORE 2007 MAY HAVE OCCURRED AT ANY TIME BEFORE 2007. THE CORRECT EFFECTIVE DATE MAY BE DIFFERENT FROM THE ONE RECORDED.

Effective date: 20050406