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EP0009564B1 - Cycle de graissage pour moteur à combustion interne - Google Patents

Cycle de graissage pour moteur à combustion interne Download PDF

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Publication number
EP0009564B1
EP0009564B1 EP79102750A EP79102750A EP0009564B1 EP 0009564 B1 EP0009564 B1 EP 0009564B1 EP 79102750 A EP79102750 A EP 79102750A EP 79102750 A EP79102750 A EP 79102750A EP 0009564 B1 EP0009564 B1 EP 0009564B1
Authority
EP
European Patent Office
Prior art keywords
oil
lubricating
bearing points
pressure
passage
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
Application number
EP79102750A
Other languages
German (de)
English (en)
Other versions
EP0009564A1 (fr
Inventor
Heinz Dipl.-Ing. Pluequet
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.)
Kloeckner Humboldt Deutz AG
Original Assignee
Kloeckner Humboldt Deutz 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 Kloeckner Humboldt Deutz AG filed Critical Kloeckner Humboldt Deutz AG
Priority to AT79102750T priority Critical patent/ATE1074T1/de
Publication of EP0009564A1 publication Critical patent/EP0009564A1/fr
Application granted granted Critical
Publication of EP0009564B1 publication Critical patent/EP0009564B1/fr
Expired legal-status Critical Current

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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
    • F01M9/00—Lubrication means having pertinent characteristics not provided for in, or of interest apart from, groups F01M1/00 - F01M7/00
    • F01M9/10—Lubrication of valve gear or auxiliaries
    • F01M9/108—Lubrication of valve gear or auxiliaries of auxiliaries
    • 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
    • F01M1/10—Lubricating systems characterised by the provision therein of lubricant venting or purifying means, e.g. of filters
    • 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

Definitions

  • the invention relates to a lubricating oil circuit for an internal combustion engine with a lubricating oil pump, which via an oil cooler and a filter device through a main pressure line, if necessary, oil to storage locations of the internal combustion engine and to more distant storage locations of additional units, e.g. of an exhaust gas turbocharger.
  • the more distant bearing points of additional units are particularly disadvantaged, such as the bearing points of the mostly located at the top of the engine or above Exhaust gas turbocharger.
  • oil of sufficient pressure may appear in the bearing points. only with such a time delay that this does not have a disadvantageous effect during the unloaded start-up and correspondingly strongly delayed or gradual load transfer;
  • the time at which sufficient pressure oil is available is too late for rapid load transfer, as occurs in the case of immediate standby units. This can result in severe damage to the bearing points, unless special measures are taken to ensure that the oil supply starts quickly.
  • a disadvantage of this arrangement is that in this case the total amount of lubricating oil flows through the oil cooler, the pressure drop being increased due to the long line length and the pressure build-up at the distant bearing points being delayed.
  • Another disadvantage is that an oil line to the nearby bearing points of the internal combustion engine remains open at all times and the amount of lubricating oil for these bearing points continuously flows through the filter device, which further hinders a rapid build-up of pressure at the distant bearing points.
  • the object of the invention is achieved by the features listed in the characterizing part of patent claim 1.
  • patent claim 3 ensure that the more distant bearing points are supplied by the direct pressure oil line only in the start-up phase, the oil supply being provided by the latter after the start-up and sufficient pressure in the main pressure line. This ensures that all bearing points are supplied with cooled and, if necessary, filtered oil during normal operation of the internal combustion engine. If there is a relatively small amount of oil flowing through the direct pressure oil line and the distant bearings to be supplied tolerate an oil that has been heated and not recooled according to the engine operation, the direct pressure oil line and the connecting line between the main pressure line can be maintained throughout the engine's operating time and the remote storage points are eliminated.
  • the object of the invention is also achieved by the features of the characterizing part of claim 4. It is assumed that the oil can only flow back through the main pressure line in the case of bearing points protected from the outside, but this is not possible due to the shut-off device.
  • the protection against emptying the bearing points can be ensured that the Branch lines from the main pressure line and its adjoining rooms to the bearing points are designed such that their highest point is higher than all other rooms in the oil circuit. Even if the connecting line from the main pressure oil line to the more distant bearing points, e.g. an exhaust gas turbocharger via lower lying points, is still empty, the oil pressure in the connecting line due to the filled oil chambers will cause the pressure oil to build up in the connecting line just as quickly as this would be the case via a direct pressure oil line.
  • 1 denotes an internal combustion engine which is only shown in outline and which has an oil sump 2 from which a lubricating oil pump 3 can draw in oil.
  • a throttle valve or shut-off device designated 5, 5a is connected, which is connected to a main pressure line 6, in which an oil cooler 7 and a filter device 8 are installed.
  • Branch lines 9 are connected to the main pressure line 6 and lead to bearing points 10 of a crankshaft 11 and to other consumers.
  • a connection line 12 is also connected to the main pressure line 6 and leads via a changeover valve 13 to remote bearing points 14 of an exhaust gas turbocharger 15.
  • a return line 16 leads from the distant bearing points 14 into the oil sump 2.
  • a direct pressure oil line 17 is connected to the pressure port 4 of the lubricating oil pump 3 and leads to the changeover valve 13 via a leak-proof lubricating oil filter 18.
  • the changeover valve 13 is designed so that pressure in the connecting line 12, namely in the area between the main pressure line 6 and the switching valve 13, switches the latter such that a connection between the connecting line and distant bearing points 14 takes place, while in the absence of pressure or a low pressure in the Connecting line, the changeover valve 13 is switched to the switching position shown in the drawing, so that the connecting line is interrupted and the direct pressure oil line is connected to the distant bearing points.
  • the throttle valve or shut-off device is actuated by means of a servo cylinder 19, a piston 20 arranged inside the servo cylinder being acted upon by the pressure in the direct pressure oil line 17 on the one hand by a spring 21 and on the other hand via a control line 22, so that the throttle valve or shut-off device is depressurized or the lowest pressure in the direct pressure oil line is closed and opened with sufficient pressure in the pressure oil line.
  • dash-dotted lines are also shown for 3 bearing points 10 of the crankshaft 1 1 spur lines 9a, which are arranged so that they have a higher point as close as possible to the main pressure line with adjoining spaces, so that the lubricating oil system when using them Stub lines and use of a shut-off valve 5a is designed to be run-proof, in which case the direct pressure oil line 17 can be omitted.

Landscapes

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

Claims (5)

1. Circuit d'huile de lubrification pour un moteur à combustion interne avec une pompe d'huile de lubrification qui, par l'intermédiaire éventuel d'un refroidisseur d'huile et d'une installation de filtrage refoule par une canalisation principale sous pression l'huile aux emplacements de paliers du moteur à combustion interne et à des emplacements de paliers plus éloignés d'appareils annexes, par exemple d'un turbocompresseur sur les gaz d'échappement, circuit d'huile de lubrification caractérisé en ce que sur la canalisation principale sous pression (6), le plus près possible de la pompe d'huile de lubrification (3), est monté un étranglement réglable (5) ou bien un organe de fermeture réglable (5a), une canalisation d'huile sous pression directe (17) étant raccordée entre cet étranglement (5) ou bien l'organe de fermeture (5a) et la pompe d'huile de lubrification (3), cette canalisation d'huile sous pression (17), éventuellement avec interposition d'un filtre d'huile de lubrification (18) de sécurité contre la marche à vide, aboutissant aux emplacements de paliers plus éloignés (14), une canalisation de commande (22) recevant la pression entre la pompe d'huile de lubrification (3) et l'étranglement (5) ou bien l'organe de fermeture (5a) étant raccordée à l'installation de réglage (19 à 21) de l'étranglement (5) ou bien de l'organe de fermeture (5a), cette canalisation de commande (22) manoeuvrant l'installation de réglage (19 à 21) dans le sens de l'ouverture contre l'action d'un ressort (21).
2. Circuit selon la revendication 1, caractérisé en ce que la canalisation de commande (22) est raccordée à la canalisation directe d'huile sous pression (17).
3. Circuit selon l'une quelconque des revendications 1 et 2, caractérisé en ce que la canalisation directe d'huile sous pression (17) débouche dans une canalisation de liaison (12) disposée entre la canalisation principale sous pression (6) et les autres emplacements de paliers éloignés (14), tandis qu'à l'emplacement où débouche cette canalisation directe sous pression (17) est installée une soupape de commutation (13) qui est actionnée par la pression dans la canalisation de liaison (12) entre la soupape de commutation (13) et la canalisation principale sous pression (6) de façon telle qu'à partir d'une pression prédéterminée dans la canalisation de liaison (12) la canalisation directe d'huile sous pression (17) est raccordée et la canalisation de liaison (12) est reliée avec les autres emplacements de paliers éloignés (14), cependant que pour une pression insuffisante, la canalisation de liaison (12) est fermée et la canalisation directe d'huile sous pression (17) est reliée avec les autres emplacements de paliers éloignés (14).
4. Circuit selon la revendication 1, caractérisé en ce que sur la canalisation principale sous pression (6) le plus près possible de la pompe d'huile de lubrification (3) est installé un grgane de fermeture réglable (5a) qui est susceptible d'être actionné dans le sens de l'ouverture contre l'action d'un ressort (21) par la pression dans la canalisation principale sous pression (6) en amont de l'organe de fermeture (5a), le refroidisseur d'huile (7), l'installation de filtrage (8) et d'autres capacités ainsi que la canalisation principale sous pression (6) avec les capacités annexes vis-à-vis des emplacements de paliers (10) du moteur à combustion interne (1) étant réalisées de façon à être protégées contre le fonctionnement à vide ou bien l'écoulement.
5. Circuit selon la revendication 4, caractérisé en ce que les canalisations de piquage (9a) disposées entre la canalisation principale sous pression (6) et les emplacements de paliers (10) du moteur à combustion interne (1) comportent le plus possible des emplacements de paliers (10) un tronçon de canalisation placé plus haut que la canalisation sous pression principale (6) et ses capacités annexes.
EP79102750A 1978-10-04 1979-08-01 Cycle de graissage pour moteur à combustion interne Expired EP0009564B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT79102750T ATE1074T1 (de) 1978-10-04 1979-08-01 Schmieroelkreislauf fuer eine brennkraftmaschine.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE2843248 1978-10-04
DE2843248A DE2843248C2 (de) 1978-10-04 1978-10-04 Schmierölkreislauf für eine Brennkraftmaschine

Publications (2)

Publication Number Publication Date
EP0009564A1 EP0009564A1 (fr) 1980-04-16
EP0009564B1 true EP0009564B1 (fr) 1982-05-19

Family

ID=6051352

Family Applications (1)

Application Number Title Priority Date Filing Date
EP79102750A Expired EP0009564B1 (fr) 1978-10-04 1979-08-01 Cycle de graissage pour moteur à combustion interne

Country Status (4)

Country Link
US (2) US4331112A (fr)
EP (1) EP0009564B1 (fr)
AT (1) ATE1074T1 (fr)
DE (1) DE2843248C2 (fr)

Families Citing this family (30)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3170777D1 (en) * 1980-12-29 1985-07-04 Norman Holding Valve gear lubrication for an internal combustion engine
JPS57173513A (en) * 1981-04-17 1982-10-25 Nippon Soken Inc Variable valve engine
EP0102080B2 (fr) * 1982-09-01 1992-12-02 Bayerische Motoren Werke Aktiengesellschaft, Patentabteilung AJ-3 Dispositif de conditionnement de quantité de l'huile pour des machines d'entraînement
US4513705A (en) * 1983-12-02 1985-04-30 Evans John W Pressurized lubrication assembly for the center bearing of a turbocharger
US4513704A (en) * 1983-12-02 1985-04-30 Evans John W Pressurized lubrication assembly for machinery having a flow restrictor device
US4628877A (en) * 1985-07-11 1986-12-16 Lubrication Research, Inc. Vehicle cold start system
US4875551A (en) * 1987-10-13 1989-10-24 R. P. M. Industries Pre-lubricant oil pressure adapter
US5000143A (en) * 1990-03-15 1991-03-19 Lubrication Research, Inc. Engine lubrication system with shared oil filter
DE4244324A1 (de) * 1992-12-28 1994-06-30 Kloeckner Humboldt Deutz Ag Hubkolbenbrennkraftmaschine
DE4431088A1 (de) * 1994-09-01 1996-03-07 Kloeckner Humboldt Deutz Ag Ölabsaugung für Abgasturbolader
DE19546924A1 (de) * 1995-12-15 1997-06-19 Deutz Ag Kolben-Brennkraftmaschine
US7150286B2 (en) * 1997-10-30 2006-12-19 Rpm Industries, Inc. Methods and systems for performing, monitoring and analyzing multiple machine fluid processes
US6708710B1 (en) * 1997-10-30 2004-03-23 Rpm Industries, Inc. Vehicle fluid change apparatus and method
US9062575B2 (en) * 1997-10-30 2015-06-23 RPM Industries, LLC Methods and systems for performing, monitoring and analyzing multiple machine fluid processes
US6988506B1 (en) 1997-10-30 2006-01-24 Rpm Industries, Inc. Fluid transfer system
US6481530B1 (en) * 2000-09-25 2002-11-19 Jim Helbig Engine pre-lubrication system
DE10159104B4 (de) 2001-12-01 2004-06-03 Dr.Ing.H.C. F. Porsche Ag Brennkraftmaschine
GB0218849D0 (en) * 2002-08-14 2002-09-25 Rolls Royce Plc Lubrication system for gas turbine engine
US6853954B2 (en) 2002-09-24 2005-02-08 John K. Apostolides Methods and systems for collecting and processing data in association with machine operation and maintenance
US20070234997A1 (en) * 2006-04-06 2007-10-11 Prenger Nicholas J Turbocharger oil supply passage check valve and method
US8015810B2 (en) * 2007-05-14 2011-09-13 GM Global Technology Operations LLC Control of turbocharger lubrication for hybrid electric vehicle
DE102007044524A1 (de) * 2007-09-18 2009-03-19 Man Diesel Se Einrichtung und Verfahren zum Reinigen von Schmiermitteln sowie Schmiermittelkreislauf
US8235022B2 (en) * 2009-02-02 2012-08-07 Ford Global Technologies Oil supply system for internal combustion engine
DE102010023063B4 (de) * 2010-06-08 2022-05-19 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Ölversorgungssystem für eine Brennkraftmaschine
US8959911B2 (en) * 2011-10-06 2015-02-24 GM Global Technology Operations LLC Engine assembly including fluid control to boost mechanism
RU2491428C1 (ru) * 2012-04-09 2013-08-27 Государственное Научное Учреждение "Объединенный Институт Машиностроения Национальной Академии Наук Беларуси" Система смазки двигателя внутреннего сгорания
DE102013203042A1 (de) * 2012-04-17 2013-10-17 Ford Global Technologies, Llc Turbolader für einen Verbrennungsmotor und Verfahren zum Betreiben eines turbogeladenen Verbrennungsmotors
EP2873832B1 (fr) * 2012-07-11 2019-02-20 Kawasaki Jukogyo Kabushiki Kaisha Structure de montage de compresseur volumétrique pour moteur
MY173690A (en) * 2012-11-07 2020-02-17 Nissan Motor Oil supply device for internal combustion engine
RU2758740C1 (ru) * 2021-02-24 2021-11-01 Федеральное автономное учреждение "25 Государственный научно-исследовательский институт химмотологии Министерства обороны Российской Федерации" Автоматизированная система управления процессом смазки поршневого двигателя внутреннего сгорания

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT103820B (de) * 1924-08-20 1926-07-26 Daimler Motoren Kreislaufschmiereinrichtung an Verbrennungskraftmaschinen mit Ladeverdichter.
GB347848A (en) * 1930-04-05 1931-05-07 Daimler Co Ltd Improvements in or relating to lubrication systems of internal combustion engines
US3057406A (en) * 1958-03-28 1962-10-09 Halliburton Co Control apparatus for use in wells
US3057436A (en) * 1960-09-01 1962-10-09 Caterpillar Tractor Co System for lubrication of engine turbochargers
US3045420A (en) * 1961-05-18 1962-07-24 Gen Motors Corp Lubrication systems and protective controls for turbocharged engines
DE2456524A1 (de) * 1974-11-29 1976-08-12 Kloeckner Humboldt Deutz Ag Druckumlaufschmieroelanlage fuer brennkraftmaschinen
US4058981A (en) * 1976-06-04 1977-11-22 Caterpillar Tractor Co. Lubricating system and method for turbocharged engines
US4157744A (en) * 1977-07-18 1979-06-12 Capriotti Lawrence J Lubricating and cooling engine system component

Also Published As

Publication number Publication date
US4331112A (en) 1982-05-25
DE2843248C2 (de) 1984-08-23
ATE1074T1 (de) 1982-06-15
DE2843248A1 (de) 1980-04-30
EP0009564A1 (fr) 1980-04-16
US4453511A (en) 1984-06-12

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