EP1703094A2 - Lubricant system for combustion engine - Google Patents

Lubricant system for combustion engine Download PDF

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Publication number
EP1703094A2
EP1703094A2 EP05027772A EP05027772A EP1703094A2 EP 1703094 A2 EP1703094 A2 EP 1703094A2 EP 05027772 A EP05027772 A EP 05027772A EP 05027772 A EP05027772 A EP 05027772A EP 1703094 A2 EP1703094 A2 EP 1703094A2
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EP
European Patent Office
Prior art keywords
oil
lubricating oil
pump
lubricating
cooler
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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
EP05027772A
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German (de)
French (fr)
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EP1703094B1 (en
EP1703094A3 (en
Inventor
Antonius Rehr
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Dr Ing HCF Porsche AG
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Dr Ing HCF Porsche AG
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Publication of EP1703094A2 publication Critical patent/EP1703094A2/en
Publication of EP1703094A3 publication Critical patent/EP1703094A3/en
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Publication of EP1703094B1 publication Critical patent/EP1703094B1/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
    • 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
    • F01M5/00—Heating, cooling, or controlling temperature of lubricant; Lubrication means facilitating engine starting
    • F01M5/002—Cooling
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M11/00—Component parts, details or accessories, not provided for in, or of interest apart from, groups F01M1/00 - F01M9/00
    • F01M11/0004—Oilsumps
    • F01M2011/0037—Oilsumps with different oil compartments

Definitions

  • the invention relates to a lubricating oil supply device for an internal combustion engine according to the features of the preamble of patent claim 1.
  • the oil cooler is a hydraulic resistance, which leads in particular at low oil temperatures to a corresponding pressure drop.
  • Downstream consumers e.g. hydraulically adjustable camshaft adjuster or a hydraulically actuated valve lift can be adversely affected due to insufficient oil pressure or amount of oil.
  • the object of the invention is to avoid such disadvantages.
  • the oil cooler is taken out as a significant hydraulic resistance from the main oil circuit and integrated into the second rear pump stage, the lubricating oil supply to consumers can be improved.
  • the power consumption of the two oil pumps can be reduced in total, if the second pump stage, a lower oil flow rate is promoted, since then according to the hydraulic Resistance of the oil cooler is lower.
  • the oil cooler is arranged on the pressure side of the second oil pump.
  • the two oil pumps are summarized in an advantageous manner to a double oil pump with two pump stages.
  • the oil conveyed back by the ATL oil suction pump into the first construction space section can also be cooled by the oil cooler in an advantageous manner.
  • the pressure side of the ATL suction pump opens upstream of the oil cooler in the (secondary) lubricating oil circuit of the second oil pump (second pressure stage).
  • the sole FIGURE shows a hydraulic circuit diagram of a supercharged dual-row eight-cylinder engine.
  • a crankcase (not shown) of an internal combustion engine and only schematically illustrated oil collection housing, hereinafter referred to as sump 2 has a front and rear space section 2a and 2b, hereinafter referred to as the first and second oil collection space are designated.
  • a suction pipe 4 and 6 is placed, which are connected on the suction side to each of an oil pump 8 and 10.
  • the two oil pumps 8 and 10 are summarized as a double oil pump with two pump stages, the first pump stage 8 is adjustable.
  • the lubricating oil collected in the rear oil collecting space 2b is pumped by means of the second pumping stage 10 into the first oil collecting space 2a.
  • the rear lubricating oil circuit designed as a plate heat exchanger oil cooler 12 is integrated, which ensures appropriate cooling of the lubricating oil.
  • the lubricating oil present in the first oil collecting space 2a is fed to the actual consumers of the internal combustion engine.
  • These include: the main bearings of the crankshaft 14, the bearings for the four camshafts 16, the piston spray nozzles 18 (4x) and the hydraulically actuated camshaft adjuster 20 provided for both cylinder bank rows on the inlet side and switchable tappet 22 for valve lift switching (so-called Porsche VarioCamPlus system).
  • the two cylinder heads supplied lubricating oil for the camshaft 16, the camshaft adjuster 20, the switchable tappets 22 and the valve clearance compensation elements 24 via first return channels 26 in the the first oil-collecting space 2a, while the lubricating oil provided for the main bearings of the crankshaft 14 and the piston-spraying nozzles 18 is returned to the rear oil-collecting space 2b via second oil-return passages 28.
  • the exhaust gas turbocharger 30 and 32 provided for each cylinder bank row is likewise supplied with lubricating oil via the first pressure stage 8 for lubricating the drive.
  • an oil-extraction pump 34 and 36 is provided which draws the lubricating oil from the so-called catch tank 38 and 40 and conveys it back into the first oil-collecting space 2a.
  • the lubricating oil delivered by the two ATL extraction pumps 34 and 36 is also cooled accordingly via the oil cooler 12.
  • a common pressure line 42 opens into the pressure line 44 of the second pump stage 10.
  • a safety valve 46 is provided, which releases a corresponding bypass line 48, if necessary.
  • a corresponding oil filter 50 is provided with a pressure relief valve.

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

Abstract

The device has oil collecting housing (2) in which two installation space sections (2a, 2b) are formed for oil exhaust. An oil pump (8) sucks lubricating oil from the section (2a) and supplies the oil to the load e.g. crankshaft bearing. Another oil pump (10) sucks the oil from the section (2b) and supplies the oil to the section (2a). An oil cooler (12) for cooling the oil is integrated in lubricating oil circulation of the pump (10).

Description

Die Erfindung betrifft eine Schmierölversorgungseinrichtung für eine Brennkraftmaschine gemäß den Merkmalen des Oberbegriffs des Patentanspruchs 1.The invention relates to a lubricating oil supply device for an internal combustion engine according to the features of the preamble of patent claim 1.

In der DE 101 59 106 A1 , die auf die Anmelderin zurückgeht, ist eine Brennkraftmaschine mit einem Kurbelgehäuse und einem daran befestigten Ölauffanggehäuse dargestellt und beschrieben, bei der mittels einer Ölpumpe mit zwei Pumpenstufen über eine erste Pumpenstufe das in einem ersten Ölsammelraum befindliche Schmieröl zu den Verbrauchern gefördert wird, während über eine zweite Pumpenstufe in einem zweiten, hinteren Ölsammelraum befindliches Schmieröl direkt in den ersten Ölsammelraum gefördert wird. Wie weiterhin aus Fig. 3 der DE 101 59 106 A1 ersichtlich ist, wird das durch die erste Pumpenstufe zu den Verbrauchern geförderte Schmieröl durch einen Ölfilter und einen Ölkühler gereinigt und gekühlt.In the DE 101 59 106 A1 , which is attributable to the applicant, an internal combustion engine is shown and described with a crankcase and an attached oil pan, in which by means of an oil pump with two pump stages via a first pump stage which is located in a first oil collecting space lubricating oil is conveyed to the consumers, while on a second pump stage is conveyed in a second, rear oil collection space located lubricating oil directly into the first oil collection chamber. As further shown in FIG. 3 of the DE 101 59 106 A1 it can be seen, the lubricating oil delivered to the consumers through the first pumping stage is cleaned and cooled by an oil filter and an oil cooler.

Insbesondere der Ölkühler stellt einen hydraulischen Widerstand dar, der insbesondere bei niedrigen Öltemperaturen zu einem entsprechenden Druckabfall führt. Nachgeschaltete Verbraucher, wie z.B. hydraulisch verstellbare Nockenwellenversteller oder eine hydraulisch betätigbare Ventilhubumschaltung können aufgrund nicht ausreichenden Öldrucks bzw. Ölmenge nachteilig beeinflusst werden.In particular, the oil cooler is a hydraulic resistance, which leads in particular at low oil temperatures to a corresponding pressure drop. Downstream consumers, e.g. hydraulically adjustable camshaft adjuster or a hydraulically actuated valve lift can be adversely affected due to insufficient oil pressure or amount of oil.

Aufgabe der Erfindung ist es, derartige Nachteile zu vermeiden.The object of the invention is to avoid such disadvantages.

Die Aufgabe wird durch die im Patentanspruch 1 angegebenen Merkmale gelöst.The object is solved by the features specified in claim 1.

Dadurch, dass der Ölkühler als ein wesentlicher hydraulischer Widerstand aus dem Hauptölkreislauf herausgenommen und in die zweite hintere Pumpenstufe eingebunden ist, kann die Schmierölversorgung zu den Verbrauchern verbessert werden. Neben einer besseren Schmierölversorgung der Hauptverbraucher kann die Leistungsaufnahme der beiden Ölpumpen in Summe reduziert werden, wenn über die zweite Pumpenstufe ein geringerer Ölvolumenstrom gefördert wird, da dann entsprechend der hydraulische Widerstand des Ölkühlers geringer ist. Durch die Eliminierung des Ölkühlers aus dem Öl-Hauptversorgungskreislauf kann die im Hauptstrom angeordnete Ölpumpe kleiner ausgebildet werden; die Antriebsleistung der Druckstufe reduziert sich dabei in der Größenordnung des Druckverlusts des Ölkühlers.The fact that the oil cooler is taken out as a significant hydraulic resistance from the main oil circuit and integrated into the second rear pump stage, the lubricating oil supply to consumers can be improved. In addition to a better lubricating oil supply to the main consumers, the power consumption of the two oil pumps can be reduced in total, if the second pump stage, a lower oil flow rate is promoted, since then according to the hydraulic Resistance of the oil cooler is lower. By eliminating the oil cooler from the oil main supply circuit, the oil pump arranged in the main flow can be made smaller; the drive power of the pressure stage is reduced in the order of magnitude of the pressure loss of the oil cooler.

Auf vorteilhafte Art und Weise ist der Ölkühler auf der Druckseite der zweiten Ölpumpe angeordnet.Advantageously, the oil cooler is arranged on the pressure side of the second oil pump.

Eine effektive und wirkungsvolle Kühlung ergibt sich, wenn der Ölkühler als ÖI/Wasser-Plattenwärmetauscher ausgebildet ist.An effective and effective cooling results when the oil cooler is designed as oil / water plate heat exchanger.

Die beiden Ölpumpen sind auf vorteilhafte Art und Weise zu einer Doppelölpumpe mit zwei Pumpenstufen zusammengefasst.The two oil pumps are summarized in an advantageous manner to a double oil pump with two pump stages.

Bei einer Brennkraftmaschine mit Abgasturboaufladung, bei der das Laufwerk des Abgasturboladers (ATL) mit Schmieröl versorgt wird, kann auf vorteilhafte Art und Weise das von der ATL- Ölabsaugpumpe in den ersten Bauraumabschnitt zurück geförderte Öl ebenfalls durch den Ölkühler gekühlt werden. Dazu mündet die Druckseite der ATL-Absaugpumpe stromauf des Ölkühlers in den (Neben-) Schmierölkreislauf der zweiten Ölpumpe (zweite Druckstufe) ein.In an internal combustion engine with exhaust gas turbocharging, in which the drive of the exhaust gas turbocharger (ATL) is supplied with lubricating oil, the oil conveyed back by the ATL oil suction pump into the first construction space section can also be cooled by the oil cooler in an advantageous manner. For this purpose, the pressure side of the ATL suction pump opens upstream of the oil cooler in the (secondary) lubricating oil circuit of the second oil pump (second pressure stage).

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

Die einzige Figur zeigt einen Hydraulikschaltplan einer aufgeladenen zweireihigen Brennkraftmaschine mit acht Zylindern.The sole FIGURE shows a hydraulic circuit diagram of a supercharged dual-row eight-cylinder engine.

Das sich nach unten hin an ein Kurbelgehäuse (nicht dargestellt) einer Brennkraftmaschine anschließende und nur schematisch dargestellte Ölauffanggehäuse, im folgenden als Ölwanne 2 bezeichnet, weist einen vorderen und hinteren Bauraumabschnitt 2a und 2b auf, die im folgenden als erster und zweiter Ölsammelraum bezeichnet sind. In jedem der beiden Ölsammelräume 2a und 2b ist ein Saugrohr 4 und 6 platziert, die saugseitig an jeweils eine Ölpumpe 8 und 10 angeschlossen sind. Im vorliegenden Ausführungsbeispiel sind die beiden Ölpumpen 8 und 10 als eine Doppelölpumpe mit zwei Pumpenstufen zusammengefasst, wobei die erste Pumpenstufe 8 regelbar ist. Das im hinteren Ölsammelraum 2b aufgefangene Schmieröl wird mit Hilfe der zweiten Pumpenstufe 10 in den ersten Ölsammelraum 2a gepumpt. In den hinteren Schmierölkreislauf ist ein als Plattenwärmetauscher ausgebildeter Ölkühler 12 integriert, der für eine entsprechende Kühlung des Schmieröls sorgt. Über die erste Pumpenstufe 8 wird das im ersten Ölsammelraum 2a befindliche Schmieröl den eigentlichen Verbrauchern der Brennkraftmaschine zugeführt. Dazu gehören: die Hauptlager der Kurbelwelle 14, die Lager für die vier Nockenwellen 16, die Kolbenspritzdüsen 18 (4x) sowie die für beide Zylinderbankreihen auf der Einlassseite vorgesehenen hydraulisch betätigbaren Nockenwellenversteller 20 und schaltbaren Tassenstössel 22 zur Ventilhubumschaltung (sog. Porsche VarioCamPlus- System) als auch die sowohl einlassals auch auslassseitig hydraulisch betätigbaren Ventilspielausgleichselemente 24. Wie aus dem Hydraulikschaltschema erkennbar, wird das den beiden Zylinderköpfen zugeführte Schmieröl für die Nockenwelle 16, die Nockenwellenversteller 20, die schaltbaren Tassenstössel 22 und die Ventilspiel-Ausgleichselemente 24 über erste Rückführkanäle 26 in den ersten Ölsammelraum 2a zurückgeführt, während das für die Hauptlager der Kurbelwelle 14 und die Kolbenspritzdüsen 18 vorgesehene Schmieröl über zweite Ölrückführkanäle 28 in den hinteren Ölsammelraum 2b zurückgeführt ist.Downstream of a crankcase (not shown) of an internal combustion engine and only schematically illustrated oil collection housing, hereinafter referred to as sump 2, has a front and rear space section 2a and 2b, hereinafter referred to as the first and second oil collection space are designated. In each of the two oil collecting chambers 2a and 2b, a suction pipe 4 and 6 is placed, which are connected on the suction side to each of an oil pump 8 and 10. In the present embodiment, the two oil pumps 8 and 10 are summarized as a double oil pump with two pump stages, the first pump stage 8 is adjustable. The lubricating oil collected in the rear oil collecting space 2b is pumped by means of the second pumping stage 10 into the first oil collecting space 2a. In the rear lubricating oil circuit designed as a plate heat exchanger oil cooler 12 is integrated, which ensures appropriate cooling of the lubricating oil. Via the first pump stage 8, the lubricating oil present in the first oil collecting space 2a is fed to the actual consumers of the internal combustion engine. These include: the main bearings of the crankshaft 14, the bearings for the four camshafts 16, the piston spray nozzles 18 (4x) and the hydraulically actuated camshaft adjuster 20 provided for both cylinder bank rows on the inlet side and switchable tappet 22 for valve lift switching (so-called Porsche VarioCamPlus system). As can be seen from the hydraulic circuit diagram, the two cylinder heads supplied lubricating oil for the camshaft 16, the camshaft adjuster 20, the switchable tappets 22 and the valve clearance compensation elements 24 via first return channels 26 in the the first oil-collecting space 2a, while the lubricating oil provided for the main bearings of the crankshaft 14 and the piston-spraying nozzles 18 is returned to the rear oil-collecting space 2b via second oil-return passages 28.

Der für jede Zylinderbankreihe vorgesehene Abgasturbolader 30 und 32 wird ebenfalls über die erste Druckstufe 8 zur Schmierung des Laufwerks mit Schmieröl versorgt. Zur Absaugung des den beiden Abgasturboladern 30 und 32 zugeführten Schmieröls ist jeweils eine Ölabsaugpumpe 34 und 36 vorgesehen, die das Schmieröl aus dem so genannten Catch-Tank 38 und 40 absaugen und in den ersten Ölsammeiraum 2a zurückfördern. Wie aus dem Schaltschema ersichtlich, wird auch das von den beiden ATL-Absaugpumpen 34 und 36 geförderte Schmieröl über den Ölkühler 12 entsprechend gekühlt. Dazu mündet eine gemeinsame Druckleitung 42 in die Druckleitung 44 der zweiten Pumpenstufe 10 ein. Zur Begrenzung des maximalen Öldrucks ist für die erste Pumpenstufe 8 ein Sicherheitsventil 46 vorgesehen, das im Bedarfsfall eine entsprechende Bypassleitung 48 freigibt. Zur Reinigung des den Verbrauchern zugeführten Schmieröls ist ein entsprechender Ölfilter 50 mit einem Überdruckventil vorgesehen.The exhaust gas turbocharger 30 and 32 provided for each cylinder bank row is likewise supplied with lubricating oil via the first pressure stage 8 for lubricating the drive. In order to extract the lubricating oil supplied to the two exhaust-gas turbochargers 30 and 32, an oil-extraction pump 34 and 36 is provided which draws the lubricating oil from the so-called catch tank 38 and 40 and conveys it back into the first oil-collecting space 2a. As can be seen from the circuit diagram, the lubricating oil delivered by the two ATL extraction pumps 34 and 36 is also cooled accordingly via the oil cooler 12. For this purpose, a common pressure line 42 opens into the pressure line 44 of the second pump stage 10. To limit the maximum oil pressure is for the first Pump stage 8, a safety valve 46 is provided, which releases a corresponding bypass line 48, if necessary. For cleaning the consumer supplied lubricating oil, a corresponding oil filter 50 is provided with a pressure relief valve.

Claims (5)

Schmierölversorgungseinrichtung für eine Brennkraftmaschine mit einem unterhalb eines Kurbelgehäuses angeordneten Ölauffanggehäuse (2), in dem zwei Bauraumabschnitte (2a, 2b) für die Ölabsaugung ausgebildet sind, mit einer ersten Ölpumpe (8), durch die das Schmieröl aus dem ersten Bauraumabschnitt (2a) abgesaugt und zu den Verbrauchern der Brennkraftmaschine, wie z.B. Kurbelwellenlager, Nockenwellenlager etc. gefördert wird, und einer zweiten Ölpumpe (10), mit der das Schmieröl aus dem zweiten Bauraumabschnitt (2b) abgesaugt und in den ersten Bauraumabschnitt (2a) gefördert wird, sowie mit einem Ölkühler (12) zur Kühlung des Schmieröls, dadurch gekennzeichnet, dass der Ölkühler (12) im Schmierölkreislauf der zweiten Ölpumpe (10) eingebunden ist.Lubricating oil supply device for an internal combustion engine with a arranged below a crankcase oil catcher housing (2) in which two space sections (2a, 2b) are formed for the oil extraction, with a first oil pump (8) through which sucked the lubricating oil from the first space section (2a) and to the consumers of the internal combustion engine, such as crankshaft bearings, camshaft bearings, etc. is promoted, and a second oil pump (10) with which the lubricating oil from the second space section (2b) is sucked and conveyed into the first space portion (2a), and with an oil cooler (12) for cooling the lubricating oil, characterized in that the oil cooler (12) in the lubricating oil circuit of the second oil pump (10) is integrated. Schmierölversorgungseinrichtung nach Anspruch 1, dadurch gekennzeichnet, dass der Ölkühler (12) auf der Druckseite der zweiten Ölpumpe (10) angeordnet ist.Lubricating oil supply device according to claim 1, characterized in that the oil cooler (12) on the pressure side of the second oil pump (10) is arranged. Schmierölversorgungseinrichtung nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass der Ölkühler (12) als Öl/Wasser-Wärmetauscher in Plattenbauweise ausgebildet ist.Lubricating oil supply device according to claim 1 or 2, characterized in that the oil cooler (12) is designed as a plate-type oil / water heat exchanger. Schmierölversorgungseinrichtung nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die beiden Ölpumpen (8, 10) zu einer Doppelölpumpe mit zwei Pumpenstufen zusammengefasst sind.Lubricating oil supply device according to one of the preceding claims, characterized in that the two oil pumps (8, 10) are combined to form a double oil pump with two pump stages. Schmierölversorgungseinrichtung nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass mindestens eine Ölabsaugpumpe (34, 36) für einen Abgasturbolader (30, 32) vorgesehen ist, die das Schmieröl vom Abgasturbolader (30, 32) in den ersten Bauraumabschnitt (2a) zurückfördert, wobei die Rückförderung über den Ölkühler (12) erfolgt.Lubricating oil supply device according to one of the preceding claims, characterized in that at least one Ölabsaugpumpe (34, 36) for an exhaust gas turbocharger (30, 32) is provided, which conveys the lubricating oil from the exhaust gas turbocharger (30, 32) in the first space section (2a), wherein the return conveyance via the oil cooler (12) takes place.
EP05027772A 2005-03-16 2005-12-19 Lubricant system for combustion engine Ceased EP1703094B1 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102005012073A DE102005012073A1 (en) 2005-03-16 2005-03-16 Lubricating oil supply device for an internal combustion engine

Publications (3)

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EP1703094A2 true EP1703094A2 (en) 2006-09-20
EP1703094A3 EP1703094A3 (en) 2010-03-24
EP1703094B1 EP1703094B1 (en) 2011-11-23

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EP05027772A Ceased EP1703094B1 (en) 2005-03-16 2005-12-19 Lubricant system for combustion engine

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US (1) US20060207543A1 (en)
EP (1) EP1703094B1 (en)
JP (1) JP2006258099A (en)
DE (1) DE102005012073A1 (en)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103670580A (en) * 2013-11-29 2014-03-26 南车玉柴四川发动机股份有限公司 Engine oil system of high-power diesel engine
EP3351756A1 (en) * 2017-01-20 2018-07-25 MAN Diesel & Turbo SE Oil supply system and method for operating same

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102010022134A1 (en) * 2010-05-20 2011-11-24 Gm Global Technology Operations Llc (N.D.Ges.D. Staates Delaware) Oil pump module with an oil pump module housing
US8408166B1 (en) 2012-08-13 2013-04-02 Ford Global Technologies, Llc System with a heat pipe
DE102016104414A1 (en) * 2016-03-10 2017-09-14 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Oil supply system for an internal combustion engine and method for supplying oil to an internal combustion engine
BR112019008815B1 (en) * 2016-10-31 2023-05-02 Cummins Inc REDUCED PARASITIC LUBRICANT SYSTEM AND METHOD OF SUPPLYING LUBRICANT FOR AN ENGINE BEARING SYSTEM
CN106837467A (en) * 2017-02-27 2017-06-13 安徽江淮汽车集团股份有限公司 A kind of engine lubrication system
CN107269342A (en) * 2017-06-21 2017-10-20 浙江春风动力股份有限公司 A kind of motorcycle and V-type double-cylinder engine lubrication system
JP7089458B2 (en) * 2018-10-31 2022-06-22 株式会社クボタ Engine with supercharger

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB237559A (en) 1924-07-22 1925-10-29 Renault Louis Improvements in or relating to lubrication
DE4444276A1 (en) 1994-12-13 1996-06-20 Jenbacher Energiesysteme Ag Arrangement for conveying and cooling the lubricating oil of internal combustion engines
DE10159106A1 (en) 2001-12-01 2003-06-18 Porsche Ag Internal combustion engine

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4004634A (en) * 1975-05-06 1977-01-25 Universal Oil Products Company Automotive oil cooler
JPS5822977Y2 (en) * 1977-06-24 1983-05-17 株式会社クボタ Lubricating oil cooling system for water-cooled engine with exhaust turbocharger
US4248293A (en) * 1979-01-16 1981-02-03 Honda Giken Kogyo Kabushiki Kaisha Apparatus for cooling engine oil
JP2539260B2 (en) * 1988-12-03 1996-10-02 マツダ株式会社 DOHC engine camshaft thrust regulation structure
SE509078C2 (en) * 1993-10-13 1998-11-30 Kvaerner Hymac Inc Uninterrupted lubrication system for a machine
US5568842A (en) * 1994-09-02 1996-10-29 Otani; Akesama Oil control unit for high-performance vehicles
JP3971082B2 (en) * 2000-05-11 2007-09-05 本田技研工業株式会社 Lubricating device for internal combustion engine
US20030151030A1 (en) * 2000-11-22 2003-08-14 Gurin Michael H. Enhanced conductivity nanocomposites and method of use thereof
DE10159104B4 (en) * 2001-12-01 2004-06-03 Dr.Ing.H.C. F. Porsche Ag Internal combustion engine
DE10159090C2 (en) * 2001-12-01 2003-09-11 Porsche Ag Oil collecting device and oil pump for an internal combustion engine
JP5020765B2 (en) * 2007-09-29 2012-09-05 本田技研工業株式会社 Power unit for motorcycle

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB237559A (en) 1924-07-22 1925-10-29 Renault Louis Improvements in or relating to lubrication
DE4444276A1 (en) 1994-12-13 1996-06-20 Jenbacher Energiesysteme Ag Arrangement for conveying and cooling the lubricating oil of internal combustion engines
DE10159106A1 (en) 2001-12-01 2003-06-18 Porsche Ag Internal combustion engine

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103670580A (en) * 2013-11-29 2014-03-26 南车玉柴四川发动机股份有限公司 Engine oil system of high-power diesel engine
CN103670580B (en) * 2013-11-29 2015-09-16 南车玉柴四川发动机股份有限公司 A kind of lubricating oil system of high-power diesel engine
EP3351756A1 (en) * 2017-01-20 2018-07-25 MAN Diesel & Turbo SE Oil supply system and method for operating same

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EP1703094B1 (en) 2011-11-23
JP2006258099A (en) 2006-09-28
US20060207543A1 (en) 2006-09-21
EP1703094A3 (en) 2010-03-24

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