EP0811765A2 - Internal combustion engine with two-stage internal gear pump - Google Patents

Internal combustion engine with two-stage internal gear pump Download PDF

Info

Publication number
EP0811765A2
EP0811765A2 EP97106781A EP97106781A EP0811765A2 EP 0811765 A2 EP0811765 A2 EP 0811765A2 EP 97106781 A EP97106781 A EP 97106781A EP 97106781 A EP97106781 A EP 97106781A EP 0811765 A2 EP0811765 A2 EP 0811765A2
Authority
EP
European Patent Office
Prior art keywords
pressure
combustion engine
hydraulic circuit
internal combustion
valve
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
EP97106781A
Other languages
German (de)
French (fr)
Other versions
EP0811765A3 (en
EP0811765B1 (en
Inventor
Rudolf Dr. Flier
Derek John Pelly
Anton Finkenzeller
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.)
Bayerische Motoren Werke AG
Original Assignee
Bayerische Motoren Werke 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 Bayerische Motoren Werke AG filed Critical Bayerische Motoren Werke AG
Publication of EP0811765A2 publication Critical patent/EP0811765A2/en
Publication of EP0811765A3 publication Critical patent/EP0811765A3/en
Application granted granted Critical
Publication of EP0811765B1 publication Critical patent/EP0811765B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C11/00—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations
    • F04C11/001—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations of similar working principle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/06—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
    • F04C2/103—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member one member having simultaneously a rotational movement about its own axis and an orbital movement

Definitions

  • the invention relates to an internal combustion engine with separate hydraulic circuits described in the preamble of claim 1.
  • Such an internal combustion engine with two separate hydraulic circuits is known, for example, from EP-B 0 416 463, which, in addition to a hydraulic circuit which forms the lubrication system of the machine, comprises a hydraulic circuit which serves to control / regulate a camshaft angle of rotation adjustment device.
  • Each of the hydraulic circuits is equipped with a pump which is driven separately by the internal combustion engine, namely with a lubricating oil pump driven by the crankshaft and a high pressure pump driven by the camshaft of the internal combustion engine.
  • the invention is based on the object of demonstrating a pump arrangement which is favorable in terms of installation space and drive expenditure for a generic internal combustion engine with separate hydraulic circuits supplied with lubricating oil, in particular of different pressures.
  • patent claim 1 being characterized by the use of a two-stage internal rotor gear pump by means of an intermediate rotor with separate pressure connections, each pressure chamber being connected to the respective suction chamber via a pressure relief valve integrated in the pump housing.
  • valve-controlled internal combustion engine it is proposed for a valve-controlled internal combustion engine that the other hydraulic circuit is used to control a valve train adjusting device, in particular a camshaft angle of rotation adjusting device, the hydraulic circuits separated in the two-stage internal rotor gear pump being advantageously used for different pressures, the control / regulating pressure is chosen to be greater than the delivery pressure for the lubrication system.
  • the hydraulic system according to the invention with a two-stage internal rotor gear pump for separate hydraulic circuits further enables the advantageous embodiment that the lubrication system hydraulic circuit with a hydraulic 4/2-way valve when the pressure drops below a predetermined minimum pressure the valve train adjustment device can be connected, this directional valve also being integrated in the pump housing in order to avoid complex pressure lines.
  • a designated with two-stage internal rotor gear pump comprises an externally toothed inner rotor 2, which cooperates with an internally and externally toothed intermediate rotor 3, which in turn engages in an outer rotor 5 with internal teeth, which is rotatably mounted in a pump housing 4.
  • Separate pressure connections 6, 7 are in oil-carrying connection with a respective pressure chamber 8, 9.
  • a common inlet 12 is provided for suction chambers 10, 11, via which lubricating oil is drawn in from an oil pan 13 of an internal combustion engine, which is only indicated schematically in FIG.
  • the pressure chamber 8 or the pressure connection 6 of the pump stage 15 is in an oil-carrying connection in a first hydraulic circuit 16 with the associated suction chamber 10 or the inlet 12 via a pressure limiting valve 17.
  • the pressure chamber 9 or the pressure connection 7 of the second pump stage 19 is connected to the suction chamber 11 or the inlet 12 via a pressure relief valve 20.
  • the pressure relief valves 17, 20 including the connection channels are integrated in the pump housing 4.
  • the first hydraulic circuit 16 with the pump stage 15 forms the lubrication system of the internal combustion engine 14.
  • the separate second hydraulic circuit 18 with the pump stage 19 serves to supply a further consumer 21, preferably to control a valve train adjusting device, in particular a camshaft angle of rotation adjustment device.
  • the pressure limiting valve 17 is preferably set to a pressure of 4-5 bar, whereas the pressure limiting valve 20 in the second hydraulic circuit 18 for the valve train adjusting device 21 is set to a pressure of 7-9 bar, for example.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Lubrication Of Internal Combustion Engines (AREA)
  • Valve Device For Special Equipments (AREA)
  • Rotary Pumps (AREA)

Abstract

The engine comprises a two-stage internal runner gear wheel pump (1) with an intermediate runner (3), with separate pressure connections (6,7). Each pressure chamber (8,9) via a pressure limiting valve (7,20) integrated in the pump housing (4) is connected with the suction chamber (10,11). The second hydraulic circuit is used for the control and regulation of a valve drive-adjustment device, particularly a camshaft rotary angle adjustment device. The control and regulating pressure (P2) is greater than the delivery pressure (P1) for the lubrication system. The lubricating system hydraulic circuit, when a predetermined minimal pressure is not reached, is connectable via a controllable 4/2 path valve with the hydraulic circuit of the adjustment device. The path valve is integrated in the pump housing (4).

Description

Die Erfindung bezieht sich auf eine im Oberbegriff des Patentanspruches 1 beschriebene Brennkraftmaschine mit gesonderten Hydraulikkreisen.The invention relates to an internal combustion engine with separate hydraulic circuits described in the preamble of claim 1.

Eine derartige Brennkraftmaschine mit zwei gesonderten Hydraulikkreisen ist beispielsweise aus der EP-B 0 416 463 bekannt, die neben einem das Schmiersystem der Maschine bildenden Hydraulikkreis einen der Steuerung/Regelung einer Nockenwellen-Drehwinkel-Verstellvorrichtung dienenden Hydraulikkreis umfaßt. Jeder der Hydraulikkreise ist mit einer von der Brennkraftmaschine gesondert angetriebenen Pumpe ausgerüstet, nämlich mit einer von der Kurbelwelle angetriebenen Schmierölpumpe und einer von der Nockenwelle der Brennkraftmaschine angetriebenen Hochdruckpumpe.Such an internal combustion engine with two separate hydraulic circuits is known, for example, from EP-B 0 416 463, which, in addition to a hydraulic circuit which forms the lubrication system of the machine, comprises a hydraulic circuit which serves to control / regulate a camshaft angle of rotation adjustment device. Each of the hydraulic circuits is equipped with a pump which is driven separately by the internal combustion engine, namely with a lubricating oil pump driven by the crankshaft and a high pressure pump driven by the camshaft of the internal combustion engine.

Nachteilig hierbei ist der erforderliche Einbauraum für die gesondert angeordneten Pumpen sowie der Aufwand an mechanischen Antriebsverbindungen, wie dies sich beispielsweise durch eine Zusammenschau einer gemäß der DE-A 38 40 356 als Schmierpumpe für eine Brennkraftmaschine dienenden, einstufigen Innenläufer-Zahnradpumpe und einer gemäß der EP-A 0 712 997 zur hydraulischen Betätigung einer Ventiltrieb-Verstellvorrichtung vorgesehenen, einstufigen Innenläufer-Zahnradpumpe veranschaulichen läßt.Disadvantages here are the required installation space for the separately arranged pumps and the outlay on mechanical drive connections, as can be seen, for example, from a summary of a single-stage internal rotor gear pump that serves as a lubrication pump for an internal combustion engine according to DE-A 38 40 356 and one according to EP -A 0 712 997 for the hydraulic actuation of a valve train adjusting device provided, single-stage internal rotor gear pump can be illustrated.

Der Erfindung liegt die Aufgabe zugrunde, für eine gattungsgemäße Brennkraftmaschine mit mittels Schmieröl versorgten gesonderten Hydraulikkreisen von insbesondere unterschiedlichen Drücken eine hinsichtlich Einbauraum und Antriebsaufwand günstige Pumpenanordnung aufzuzeigen.The invention is based on the object of demonstrating a pump arrangement which is favorable in terms of installation space and drive expenditure for a generic internal combustion engine with separate hydraulic circuits supplied with lubricating oil, in particular of different pressures.

Diese Aufgabe ist mit dem Patentanspruch 1 gelöst, wobei die Erfindung sich kennzeichnet durch die Verwendung einer mittels eines Zwischenläufers zweistufigen Innenläufer-Zahnradpumpe mit gesonderten Druckanschlüssen, wobei jede Druckkammer über ein im Pumpengehäuse integriertes Druckbegrenzungsventil mit der jeweiligen Saugkammer in Verbindung steht.This object is achieved with patent claim 1, the invention being characterized by the use of a two-stage internal rotor gear pump by means of an intermediate rotor with separate pressure connections, each pressure chamber being connected to the respective suction chamber via a pressure relief valve integrated in the pump housing.

Der Einsatz einer derartigen, beispielsweise aus der DE-C 35 20 884 per se bekannten zweistufigen Innenläufer-Zahnradpumpe in einer gegenüber diesem Stand der Technik bezüglich der Versorgung gesonderter Hydraulikkreise mit insbesondere unterschiedlichen Drücken vorteilhaft weitergebildeten Ausführung ergibt in vorteilhafter Weise einen reduzierten Einbauraum sowie einen minimierten Antriebsaufwand. Die in einer Drehebene angeordneten drei Läufer bzw. Rotoren der Innenläufer-Zahnradpumpe ergeben in Verbindung mit den im Pumpengehäuse baulich integrierten Druckbegrenzungsventilen eine für einen reduzierten Einbauraum vorteilhaft kleinbauende Pumpe, die weiter mittels lediglich einer einzigen Antriebswelle einen wesentlich minimierten Antriebsaufwand ergibt.The use of such a two-stage internal rotor gear pump, known per se, for example from DE-C 35 20 884, in an embodiment which is advantageously further developed compared to this prior art with regard to the supply of separate hydraulic circuits with, in particular, different pressures, advantageously results in a reduced installation space and a minimized one Drive effort. The three rotors or rotors of the internal rotor gear pump, which are arranged in a rotating plane, in combination with the pressure relief valves integrated in the pump housing, result in a pump that is advantageously small in size for a reduced installation space and furthermore results in a significantly minimized drive expenditure by means of only a single drive shaft.

In Ausgestaltung der Erfindung wird für eine ventilgesteuerte Brennkraftmaschine vorgeschlagen, daß der andere Hydraulikkreis der Steuerung/Regelung einer Ventiltrieb-Verstellvorrichtung, insbesondere einer Nockenwellen-Drehwinkel-Verstellvorrichtung dient, wobei die in der zweistufigen Innenläufer-Zahnradpumpe getrennten Hydraulikkreise vorteilhafterweise für unterschiedliche Drücke genutzt sind, wobei der Steuer-/Regeldruck gegenüber dem Förderdruck für das Schmiersystem größer gewählt ist.In an embodiment of the invention, it is proposed for a valve-controlled internal combustion engine that the other hydraulic circuit is used to control a valve train adjusting device, in particular a camshaft angle of rotation adjusting device, the hydraulic circuits separated in the two-stage internal rotor gear pump being advantageously used for different pressures, the control / regulating pressure is chosen to be greater than the delivery pressure for the lubrication system.

Das erfindungsgemäße Hydrauliksystem mit einer zweistufigen Innenläufer-Zahnradpumpe für gesonderte Hydraulikkreise ermöglicht weiter die vorteilhafte Ausgestaltung, daß der Schmiersystem-Hydraulikkreis bei Unterschreiten eines vorbestimmten Minimaldruckes über ein ansteuerbares 4-/2-Wegeventil mit dem Hydraulikkreis der Ventiltrieb-Verstellvorrichtung verbindbar ist, wobei dieses Wegeventil zur Vermeidung aufwendig angeordneter Druckleitungen ebenfalls im Pumpengehäuse integriert angeordnet ist.The hydraulic system according to the invention with a two-stage internal rotor gear pump for separate hydraulic circuits further enables the advantageous embodiment that the lubrication system hydraulic circuit with a hydraulic 4/2-way valve when the pressure drops below a predetermined minimum pressure the valve train adjustment device can be connected, this directional valve also being integrated in the pump housing in order to avoid complex pressure lines.

Die Erfindung ist anhand der Zeichnung beschrieben. Es zeigt

Figur 1
eine zweistufige Innenläufer-Zahnradpumpe,
Figur 2
einen Hydraulikplan zu dieser Zahnradpumpe für gesonderte Hydraulikkreise einer Brennkraftmaschine.
The invention is described with reference to the drawing. It shows
Figure 1
a two-stage internal rotor gear pump,
Figure 2
a hydraulic plan for this gear pump for separate hydraulic circuits of an internal combustion engine.

Eine mit 1 bezeichnete, zweistufige Innenläufer-Zahnradpumpe umfaßt einen außenverzahnten Innenläufer 2, der mit einem innen- und außen-verzahnten Zwischenläufer 3 zusammenwirkt, der seinerseits in einen in einem Pumpengehäuse 4 drehbeweglich gelagerten Außenläufer 5 mit Innenverzahnung eingreift. Getrennte Druckanschlüsse 6, 7 stehen mit einer jeweiligen Druckkammer 8, 9 in ölführender Verbindung. Für Saugkammern 10, 11 ist ein gemeinsamer Zulauf 12 vorgesehen, über den Schmieröl aus einer Ölwanne 13 einer lediglich in Figur 2 schematisch angedeuteten, mit 14 bezeichneten Brennkraftmaschine angesaugt ist.A designated with two-stage internal rotor gear pump comprises an externally toothed inner rotor 2, which cooperates with an internally and externally toothed intermediate rotor 3, which in turn engages in an outer rotor 5 with internal teeth, which is rotatably mounted in a pump housing 4. Separate pressure connections 6, 7 are in oil-carrying connection with a respective pressure chamber 8, 9. A common inlet 12 is provided for suction chambers 10, 11, via which lubricating oil is drawn in from an oil pan 13 of an internal combustion engine, which is only indicated schematically in FIG.

Wie aus den Figuren 1 und 2 ersichtlich, steht die Druckkammer 8 bzw. der Druckanschluß 6 der Pumpenstufe 15 in einem ersten Hydraulikkreis 16 mit der zugeordneten Saugkammer 10 bzw. dem Zulauf 12 über ein Druckbegrenzungsventil 17 in ölführender Verbindung. Im zweiten Hydraulikkreis 18 steht die Druckkammer 9 bzw. der Druckanschluß 7 der zweiten Pumpenstufe 19 mit der Saugkammer 11 bzw. dem Zulauf 12 über ein Druckbegrenzungsventil 20 in Verbindung. Zur Einsparung gesonderter Leitungen sind die Druckbegrenzungsventile 17, 20 einschließlich der Verbindungskanäle in dem Pumpengehäuse 4 integriert angeordnet.As can be seen from FIGS. 1 and 2, the pressure chamber 8 or the pressure connection 6 of the pump stage 15 is in an oil-carrying connection in a first hydraulic circuit 16 with the associated suction chamber 10 or the inlet 12 via a pressure limiting valve 17. In the second hydraulic circuit 18, the pressure chamber 9 or the pressure connection 7 of the second pump stage 19 is connected to the suction chamber 11 or the inlet 12 via a pressure relief valve 20. To save on separate lines, the pressure relief valves 17, 20 including the connection channels are integrated in the pump housing 4.

Gemäß dem Hydraulikplan nach Figur 2 bildet der erste Hydraulikkreis 16 mit der Pumpenstufe 15 das Schmiersystem der Brennkraftmaschine 14. Der gesonderte zweite Hydraulikkreis 18 mit der Pumpenstufe 19 dient der Versorgung eines weiteren Verbrauchers 21, vorzugsweise der Steuerung/Regelung einer Ventiltrieb-Verstellvorrichtung, insbesondere einer Nockenwellen-Drehwinkel-Verstellvorrichtung.According to the hydraulic plan according to FIG. 2, the first hydraulic circuit 16 with the pump stage 15 forms the lubrication system of the internal combustion engine 14. The separate second hydraulic circuit 18 with the pump stage 19 serves to supply a further consumer 21, preferably to control a valve train adjusting device, in particular a camshaft angle of rotation adjustment device.

Für den Hydraulikkreis 16 des Schmiersystems der Brennkraftmaschine 14 ist das Druckbegrenzungsventil 17 vorzugsweise auf einen Druck von 4 - 5 bar eingestellt, wogegen das Druckbegrenzungsventil 20 im zweiten Hydraulikkreis 18 für die Ventiltrieb-Verstellvorrichtung 21 beispielsweise auf einen Druck von 7 - 9 bar eingestellt ist.For the hydraulic circuit 16 of the lubrication system of the internal combustion engine 14, the pressure limiting valve 17 is preferably set to a pressure of 4-5 bar, whereas the pressure limiting valve 20 in the second hydraulic circuit 18 for the valve train adjusting device 21 is set to a pressure of 7-9 bar, for example.

Der erfindungsgemäße Einsatz der zweistufigen Innenläufer-Zahnradpumpe 1 an einer Brennkraftmaschine 14 zur Versorgung ihres Schmiersystems einerseits und einer Ventiltrieb-Verstellvorrichtung 21 andererseits ergibt neben einem minimierten Antriebsaufwand mit einer einzigen Antriebswelle für die drei Läufer bzw. Rotoren 2, 3 und 5 in einer Drehebene eine kurzbauende Pumpe 1, die durch Integration der Druckbegrenzungs- bzw. Druckregelventile 17, 20 einschließlich der Verbindungskanäle eine kompakte Ausgestaltung mit keinem Einbauraum ergibt.The inventive use of the two-stage internal rotor gear pump 1 on an internal combustion engine 14 for supplying its lubrication system on the one hand and a valve drive adjusting device 21 on the other hand results in a minimized drive effort with a single drive shaft for the three rotors or rotors 2, 3 and 5 in one plane of rotation short pump 1, which by integrating the pressure limiting or pressure control valves 17, 20 including the connecting channels results in a compact design with no installation space.

Weiter ist mit dem erfindungsgemäßen Einsatz der zweistufigen Innenläufer-Zahnradpumpe 1 für gesonderte Hydraulikkreise 16, 18 mit unterschiedlichen Drücken P1 und P2 die Möglichkeit eröffnet, im Betrieb der Brennkraftmaschine 14 dem Schmiersystem-Hydraulikkreis 16 Priorität dadurch einzuräumen, daß dieser Schmiersystem-Hydraulikkreis 16 bei Unterschreiten eines vorbestimmten Minimaldruckes - z.B. ca. 2 bar - über ein ansteuerbares 4-/2-Wege-Ventil 22 mit dem Hydraulikkreis 18 der Ventiltrieb-Verstellvorrichtung 21 verbindbar ist. Zur Vermeidung aufwendig angeordneter Druckleitungen ist dieses Wege-Ventil 22 ebenfalls im Pumpengehäuse 4 integriert.Furthermore, with the use according to the invention of the two-stage internal rotor gear pump 1 for separate hydraulic circuits 16, 18 with different pressures P 1 and P 2, the possibility is given to give priority to the lubrication system hydraulic circuit 16 during operation of the internal combustion engine 14 in that this lubrication system hydraulic circuit 16 if the pressure falls below a predetermined minimum pressure - for example approx. 2 bar - can be connected to the hydraulic circuit 18 of the valve train adjusting device 21 via a controllable 4- / 2-way valve 22. To avoid elaborately arranged pressure lines, this directional valve 22 is also integrated in the pump housing 4.

Claims (3)

Brennkraftmaschine mit mittels Schmieröl versorgten gesonderten Hydraulikkreisen, - wobei jedem Hydraulikkreis (16, 18) eine Pumpe (15, 19) zugeordnet ist, und - einer der Hydraulikkreise (16) das Schmiersystem der Brennkraftmaschine (14) bildet, - gekennzeichnet durch die Verwendung einer mittels eines Zwischenläufers (3) zweistufigen Innenläufer-Zahnradpumpe (1) mit gesonderten Druckanschlüssen (6, 7), wobei - jede Druckkammer (8 ,9) über ein im Pumpengehäuse (4) integriertes Druckbegrenzungsventil (17, 20) mit der jeweiligen Saugkammer (10, 11) in Verbindung steht. Internal combustion engine with separate hydraulic circuits supplied with lubricating oil, - With each hydraulic circuit (16, 18) a pump (15, 19) is assigned, and - One of the hydraulic circuits (16) forms the lubrication system of the internal combustion engine (14), - characterized by the use of an intermediate rotor (3) two-stage internal rotor gear pump (1) with separate pressure connections (6, 7), whereby - Each pressure chamber (8, 9) is connected to the respective suction chamber (10, 11) via a pressure relief valve (17, 20) integrated in the pump housing (4). Brennkraftmaschine nach Anspruch 1, mit einem Ventiltrieb, dadurch gekennzeichnet, - daß der andere Hydraulikkreis (18) der Steuerung/Regelung einer Ventiltrieb-Verstellvorrichtung (21), insbesondere einer Nockenwellen-Drehwinkel-Verstellvorrichtung dient, wobei - der Steuer-/Regeldruck (P2) gegenüber dem Förderdruck (P1) für das Schmiersystem größer gewählt ist. Internal combustion engine according to claim 1, with a valve train, characterized in that - That the other hydraulic circuit (18) is used to control a valve train adjusting device (21), in particular a camshaft angle of rotation adjusting device, wherein - The control pressure (P 2 ) compared to the delivery pressure (P 1 ) for the lubrication system is selected larger. Brennkraftmaschine nach Anspruch 2, dadurch gekennzeichnet, - daß der Schmiersystem-Hydraulikkreis (16) bei Unterschreiten eines vorbestimmten Minimaldruckes über ein ansteuerbares 4-/2-Wege-Ventil (22) mit dem Hydraulikkreis (18) der Verstellvorrichtung (21) verbindbar ist und - daß das Wege-Ventil (22) im Pumpengehäuse (4) integriert angeordnet ist. Internal combustion engine according to claim 2, characterized in - That the lubrication system hydraulic circuit (16) when falling below a predetermined minimum pressure via a controllable 4- / 2-way valve (22) with the hydraulic circuit (18) of the adjusting device (21) can be connected and - That the directional valve (22) in the pump housing (4) is arranged integrated.
EP97106781A 1996-06-05 1997-04-24 Internal combustion engine with two-stage internal gear pump Expired - Lifetime EP0811765B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19622688A DE19622688A1 (en) 1996-06-05 1996-06-05 Internal combustion engine with separate hydraulic circuits supplied with lubricating oil
DE19622688 1996-06-05

Publications (3)

Publication Number Publication Date
EP0811765A2 true EP0811765A2 (en) 1997-12-10
EP0811765A3 EP0811765A3 (en) 1998-06-10
EP0811765B1 EP0811765B1 (en) 2002-08-28

Family

ID=7796286

Family Applications (1)

Application Number Title Priority Date Filing Date
EP97106781A Expired - Lifetime EP0811765B1 (en) 1996-06-05 1997-04-24 Internal combustion engine with two-stage internal gear pump

Country Status (2)

Country Link
EP (1) EP0811765B1 (en)
DE (2) DE19622688A1 (en)

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2000042321A1 (en) * 1999-01-13 2000-07-20 Valeo Electrical Systems, Inc. Hydraulic machine comprising dual gerotors
AT407563B (en) * 1998-02-26 2001-04-25 Tcg Unitech Ag OIL PUMP FOR AN INTERNAL COMBUSTION ENGINE
WO2006102948A1 (en) * 2005-03-31 2006-10-05 Gkn Driveline International Gmbh Motor vehicle hydraulic pump
EP1961961A2 (en) 2007-02-20 2008-08-27 Yamada Manufacturing Co., Ltd. Oil pump pressure control device
CN102900665A (en) * 2012-10-16 2013-01-30 李庆中 Inside engaged gear pump or gear motor device with multilayer structure
GB2516523A (en) * 2013-04-08 2015-01-28 Danfoss Power Solutions Inc Selectable flow hydraulic gear pump
CN104929930A (en) * 2015-06-18 2015-09-23 河北睿智辰诚液压机械科技有限公司 Gear pump capable of achieving high-pressure flow and low-pressure flow convergence and distribution
US9951771B2 (en) 2013-04-08 2018-04-24 Danfoss Power Solutions Inc. Selectable flow hydraulic gear pump
CN109469609A (en) * 2018-11-08 2019-03-15 奇瑞汽车股份有限公司 Lubricating oil pump and engine lubrication system
CN112879279A (en) * 2021-01-27 2021-06-01 邵玉强 Duplex internal gear pump
EP3848592A1 (en) * 2020-01-13 2021-07-14 Schwäbische Hüttenwerke Automotive GmbH Fluid supply system for supplying multiple fluid consumers of a motor vehicle with fluid

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6397796B1 (en) * 2001-03-05 2002-06-04 Ford Global Technologies, Inc. Oiling systems and methods for changing lengths of variable compression ratio connecting rods
DE10159147A1 (en) * 2001-12-01 2003-06-18 Zahnradfabrik Friedrichshafen Hydraulic gear pump has pump stages in one plane, one above other radially
DE10350632A1 (en) 2003-10-29 2005-06-16 Gkn Sinter Metals Gmbh Double or multiple pump
US7290991B2 (en) * 2004-02-18 2007-11-06 General Motors Corporation Dual oil supply pump
DE102004058261A1 (en) * 2004-12-03 2006-06-08 Volkswagen Ag Oil pump, has low pressure oil cycle provided with one of pump stages for cooling of motor vehicle gearbox with cooling oil, where oil from low pressure oil cycle is taken out for prefilling clutch with help of quantity switching mechanism
DE102021133555A1 (en) 2021-12-16 2023-06-22 Endter SinterTechnics GmbH & Co. KG Gerotor unit and pump or motor with a gerotor unit

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2830598A1 (en) * 1977-08-19 1979-03-01 Garrett Corp FLUID PUMP DEVICE
DE3520884A1 (en) * 1984-06-11 1986-01-02 Trw Inc., Cleveland, Ohio TWO-STAGE BUILT-IN CENTRIFUGAL PUMP WITH QUANTITY CONTROL
DE3812411A1 (en) * 1988-04-14 1989-10-26 Walter Schopf Series pump-step arrangement with controllable useful delivery rate for mobile use
US5247914A (en) * 1991-05-29 1993-09-28 Atsugi Unisia Corporation Intake- and/or exhaust-valve timing control system for internal combustion engines

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE933963C (en) * 1940-08-09 1955-10-06 Messerschmitt Boelkow Blohm Arrangement of auxiliary machines and devices for fuel delivery and allocation in internal combustion engines
DE2620480C2 (en) * 1976-05-08 1984-03-01 Mtu Motoren- Und Turbinen-Union Friedrichshafen Gmbh, 7990 Friedrichshafen Lubricating oil supply
DE3445454A1 (en) * 1984-12-13 1986-06-26 P.I.V. Antrieb Werner Reimers GmbH & Co KG, 6380 Bad Homburg Multistage internal-gear gear pump
DE3714087A1 (en) * 1986-05-10 1987-11-12 Volkswagen Ag Drive assembly with individual lubricating oil circuits for engine and transmission
DE3840356A1 (en) * 1987-12-05 1989-06-15 Barmag Barmer Maschf Lubricating oil pump in motor vehicles
DE3921715A1 (en) * 1989-07-01 1991-01-10 Porsche Ag DEVICE FOR DRIVING TWO OIL PUMPS ON A PISTON PISTON INTERNAL COMBUSTION ENGINE
DE3933978A1 (en) * 1989-10-11 1991-05-02 Eisenmann Siegfried A SUCTION-CONTROLLED GEAR RING PUMP
JP3531769B2 (en) * 1994-08-25 2004-05-31 アイシン精機株式会社 Oil pump device

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2830598A1 (en) * 1977-08-19 1979-03-01 Garrett Corp FLUID PUMP DEVICE
DE3520884A1 (en) * 1984-06-11 1986-01-02 Trw Inc., Cleveland, Ohio TWO-STAGE BUILT-IN CENTRIFUGAL PUMP WITH QUANTITY CONTROL
DE3812411A1 (en) * 1988-04-14 1989-10-26 Walter Schopf Series pump-step arrangement with controllable useful delivery rate for mobile use
US5247914A (en) * 1991-05-29 1993-09-28 Atsugi Unisia Corporation Intake- and/or exhaust-valve timing control system for internal combustion engines

Cited By (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT407563B (en) * 1998-02-26 2001-04-25 Tcg Unitech Ag OIL PUMP FOR AN INTERNAL COMBUSTION ENGINE
US6195990B1 (en) 1999-01-13 2001-03-06 Valeo Electrical Systems, Inc. Hydraulic machine comprising dual gerotors
WO2000042321A1 (en) * 1999-01-13 2000-07-20 Valeo Electrical Systems, Inc. Hydraulic machine comprising dual gerotors
US7946402B2 (en) 2005-03-31 2011-05-24 Gkn Driveline International Gmbh Motor vehicle hydraulic pump
WO2006102948A1 (en) * 2005-03-31 2006-10-05 Gkn Driveline International Gmbh Motor vehicle hydraulic pump
JP4833277B2 (en) * 2005-03-31 2011-12-07 ジーケイエヌ ドライブライン インターナショナル ゲゼルシャフト ミット ベシュレンクテル ハフツング Hydraulic pump for automobile
JP2008537580A (en) * 2005-03-31 2008-09-18 ジーケイエヌ ドライブライン インターナショナル ゲゼルシャフト ミット ベシュレンクテル ハフツング Hydraulic pump for automobile
EP1961961A2 (en) 2007-02-20 2008-08-27 Yamada Manufacturing Co., Ltd. Oil pump pressure control device
EP1961961A3 (en) * 2007-02-20 2009-12-16 Yamada Manufacturing Co., Ltd. Oil pump pressure control device
JP2008202488A (en) * 2007-02-20 2008-09-04 Yamada Seisakusho Co Ltd Pressure control device for oil pump
CN102900665A (en) * 2012-10-16 2013-01-30 李庆中 Inside engaged gear pump or gear motor device with multilayer structure
GB2516523A (en) * 2013-04-08 2015-01-28 Danfoss Power Solutions Inc Selectable flow hydraulic gear pump
US9951771B2 (en) 2013-04-08 2018-04-24 Danfoss Power Solutions Inc. Selectable flow hydraulic gear pump
CN104929930A (en) * 2015-06-18 2015-09-23 河北睿智辰诚液压机械科技有限公司 Gear pump capable of achieving high-pressure flow and low-pressure flow convergence and distribution
CN104929930B (en) * 2015-06-18 2017-03-01 河北睿智辰诚液压机械科技有限公司 A kind of gear pump being capable of high-low pressure confluence
CN109469609A (en) * 2018-11-08 2019-03-15 奇瑞汽车股份有限公司 Lubricating oil pump and engine lubrication system
EP3848592A1 (en) * 2020-01-13 2021-07-14 Schwäbische Hüttenwerke Automotive GmbH Fluid supply system for supplying multiple fluid consumers of a motor vehicle with fluid
CN112879279A (en) * 2021-01-27 2021-06-01 邵玉强 Duplex internal gear pump
CN112879279B (en) * 2021-01-27 2023-10-27 邵玉强 Duplex internal gear pump

Also Published As

Publication number Publication date
EP0811765A3 (en) 1998-06-10
DE19622688A1 (en) 1997-12-11
EP0811765B1 (en) 2002-08-28
DE59708039D1 (en) 2002-10-02

Similar Documents

Publication Publication Date Title
EP0811765B1 (en) Internal combustion engine with two-stage internal gear pump
EP0571472B1 (en) Hydraulic system
DE60303061T2 (en) Engine lubrication system and a method of operating the same
DE4138313C2 (en) Radial piston pump
DE19531359B4 (en) Oil pumping station
DE112007002915B4 (en) Adjustment device for phase adjustment of a camshaft
DE60317399T2 (en) Adjustable displacement pump as well as Steursystem for it
DE3523293A1 (en) AUXILIARY POWER STEERING DEVICE
DE4227037B4 (en) Hydrostatic axial piston pump
DE10237801A1 (en) Device for regulating the pressure of hydraulic pumps
DE10141786B4 (en) Device for controlling the lubricating oil pressure of an internal combustion engine
EP1394415B1 (en) Capacity controlled compressor for commercial vehicles
EP0416463B1 (en) Internal combustion engine with camshafts and a phase change mechanism
EP1463888B1 (en) Device for pressure regulation of hydraulic pumps
WO1993024346A1 (en) Hydraulic pump driven by an internal combustion engine
DE3906477C2 (en)
DE4141492A1 (en) HYDRAULIC ARRANGEMENT FOR WORKING MACHINES
DE4105144A1 (en) Six-piston radial pump - is driven by vehicle IC engine circuit providing power to servo steering, camshaft adjustment and wheel brakes
DE3432704A1 (en) Eaton pump
EP1481148B1 (en) Device for controlling charge exchange valves
EP0137899B1 (en) Control valve for a control system of a continuously variable driving belt transmission
DE102004001343A1 (en) Variable valve lift device for internal combustion engine, has rotatable eccentric shaft having eccentrics contours positioned within circle formed by external diameter of bearings of eccentric shaft
DE102020100583A1 (en) Fluid supply system for supplying several fluid consumers of a motor vehicle with fluid
EP1770000B1 (en) Motor vehicle comprising a power steering pump and an air compressor
DE10051154B4 (en) Hydraulic vehicle cover actuator assembly

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: A2

Designated state(s): DE FR GB IT

PUAL Search report despatched

Free format text: ORIGINAL CODE: 0009013

AK Designated contracting states

Kind code of ref document: A3

Designated state(s): DE FR GB IT

17P Request for examination filed

Effective date: 19981027

GRAG Despatch of communication of intention to grant

Free format text: ORIGINAL CODE: EPIDOS AGRA

GRAG Despatch of communication of intention to grant

Free format text: ORIGINAL CODE: EPIDOS AGRA

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

17Q First examination report despatched

Effective date: 20020218

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE FR GB IT

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

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

Effective date: 20020828

REF Corresponds to:

Ref document number: 59708039

Country of ref document: DE

Date of ref document: 20021002

ET Fr: translation filed
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

Effective date: 20030530

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

Ref country code: DE

Payment date: 20120615

Year of fee payment: 16

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

Ref country code: GB

Payment date: 20130425

Year of fee payment: 17

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

Ref country code: FR

Payment date: 20130605

Year of fee payment: 17

Ref country code: IT

Payment date: 20130418

Year of fee payment: 17

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: 20131101

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 59708039

Country of ref document: DE

Effective date: 20131101

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

Effective date: 20140424

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20141231

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

Ref country code: GB

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

Effective date: 20140424

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

Ref country code: FR

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

Effective date: 20140430

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

Effective date: 20140424