EP1463888B1 - Dispositif pour reguler la pression de pompes hydrauliques - Google Patents

Dispositif pour reguler la pression de pompes hydrauliques Download PDF

Info

Publication number
EP1463888B1
EP1463888B1 EP02806046A EP02806046A EP1463888B1 EP 1463888 B1 EP1463888 B1 EP 1463888B1 EP 02806046 A EP02806046 A EP 02806046A EP 02806046 A EP02806046 A EP 02806046A EP 1463888 B1 EP1463888 B1 EP 1463888B1
Authority
EP
European Patent Office
Prior art keywords
pressure
piston
control
regulating
oil
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.)
Revoked
Application number
EP02806046A
Other languages
German (de)
English (en)
Other versions
EP1463888A1 (fr
Inventor
Dieter Dipl.-Ing. Voigt
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.)
Individual
Original Assignee
Individual
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
Family has litigation
First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=27438038&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=EP1463888(B1) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Priority claimed from DE10237801A external-priority patent/DE10237801C5/de
Application filed by Individual filed Critical Individual
Publication of EP1463888A1 publication Critical patent/EP1463888A1/fr
Application granted granted Critical
Publication of EP1463888B1 publication Critical patent/EP1463888B1/fr
Anticipated expiration legal-status Critical
Revoked 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
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/18—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber
    • F04C14/185—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by varying the useful pumping length of the cooperating members in the axial direction
    • 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
    • F01M1/16—Controlling lubricant pressure or quantity
    • 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
    • F01M1/18—Indicating or safety devices
    • F01M1/20—Indicating or safety devices concerning lubricant pressure
    • 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
    • F04C2270/00—Control; Monitoring or safety arrangements
    • F04C2270/05—Speed
    • F04C2270/052—Speed angular

Definitions

  • the invention relates to devices for pressure control of hydraulic pumps, in particular for oil pumps with a flow control device for lubricating oil supply of internal combustion engines, with a control piston and a control spring for controlling the flow rate control device and with a control device for the control piston.
  • Such control devices have the task of the delivery of the hydraulic pump, and in particular an oil pump, to changing needs, e.g. the lubrication system of an internal combustion engine in terms of oil pressure and oil quantity to adapt. As a result, unnecessarily high oil pressures are avoided, as well as kept low the drive power of the lubricating oil pump in view of a good efficiency of the internal combustion engine.
  • DE-C-753580 describes an oil pump with a variable speed delivery, in which the governor of an injection pump via a mechanical coupling changes the flow rate of the oil pump.
  • Other embodiments of controllable oil pumps can be found in DE-A-37 26 800 and US-A-4,828,462.
  • a device for pressure control of hydraulic pumps with the features mentioned is proposed, which is characterized in that the control piston has an effective surface for constantly applied oil pressure and continues to be acted upon by the drive with an additional force. This causes the oil pressure to set at least in two control pressure levels.
  • the control piston which can be acted upon by a drive device with a variable force, effects the associated setting of the flow rate control device.
  • Fig. 1 shows a first embodiment of the pressure control device according to the invention for an external gear oil pump with flow control.
  • this oil pump consists of an oil pump housing 1, in which a fixed on a drive shaft 2 drive gear 3 is arranged.
  • the drive shaft 2 is mounted in a cover piston 4 associated with a cover piston 5.
  • a flow control is in a known manner relative to the drive gear 3 in meshing engagement with him sliding shift gear 6 is axially displaced, so that then by the changed meshing width, the oil flow rate is changed accordingly.
  • the sliding gear 6 is mounted on a non-rotating bolt 7, the right side a shift piston 8 and the left side carries a spring piston 9.
  • This formed composite is referred to as a displacement unit 10.
  • the shifting unit 10 is at its Displacement piston 8 constantly subjected to oil pressure, while counteracting the spring piston 9, a piston spring 11 as well as acting in the spring chamber 12, controllable control pressure make the flow control.
  • control of the control pressure acting in spring chamber 12 is made via a control bore 13 of a control piston 14, which is acted upon at its active surface 15 via a connection 16 constantly with oil pressure.
  • control position of the control piston 14 is its control pin 18 directly opposite to the control bore 13.
  • the control pin 18 is bounded on the left side by a pressure groove 19 and the right side of a relief groove 20.
  • control pin 18 is slightly narrower than the diameter of the control bore 13
  • a control pressure is adjusted in the control position shown in the spring chamber 12, which between the over another connection 21 in the pressure groove 19 applied oil pressure and one can be fed via the discharge groove 20, complete Pressure relief can be.
  • Via a diagonal bore 22 in control piston 14, the relief groove 20 is in communication with the environment.
  • control means of the control piston 14 consists of a magnetic coil 23 which exerts a magnetic additional force to the control piston 14 via a corresponding control by a control unit of the engine via its armature 24.
  • a change in the additional magnetic force can be made either continuously or stepwise demand-oriented by the control unit, which has a corresponding effect on the control of oil pressure and flow rate of the oil pump.
  • the oil pressure behind the oil filter 25 is adjusted to the desired pressure level by the pressure control of the oil pump, so that regardless of pollution caused by variable pressure losses of the oil filter 25 a reliable oil pressure is ensured for the lubrication of the engine.
  • all parts of the control device as well as all bearings of the oil pump for example, the storage of the drive shaft 2 in cover piston 5 via an oil hole 27 from the displacement chamber 28, supplied with filtered oil, so that the reliability and the life of the oil pump can be increased.
  • Fig. 2 shows another embodiment of the invention with continuously variable oil pressure control.
  • a stepping motor 29 with an adjustable spring system 30 for the control spring 17 of the now shown uncut control piston 14 is used instead of the solenoid 23 of Figure 1 here. Due to the basic position of the spring system 30 of control spring 17, which adjusts automatically without electrical control of the stepping motor 29, the maximum required operating oil pressure of, for example, 5 bar is ensured by the corresponding bias of the control spring 17.
  • the oil pressure can be lowered as needed or even further increased in special applications.
  • Fig. 3 shows a preferred embodiment of the oil pressure and flow control according to the invention using the example of an external gear oil pump, in which the control device of the control piston takes place exclusively centrifugally dependent in two speed-related control pressure stages.
  • the now formed as a stepped piston 51 control piston is derived from the control piston 14 of FIG. 1 and 2 respectively. On the left side, it has a control spring 52 and on the right side a first active surface 53, which is constantly subjected to oil pressure.
  • a right-side second active surface 54 of stepped piston 51 is also acted upon at low operating speeds of the engine with oil pressure, so that an oil pressure control at, for example, 2.5 bar of the first control pressure stage takes place by an oil pressure effect on the two active surfaces 53 and 54 and the appropriately designed control spring 52.
  • the Fig. 4 belonging to Fig. 4 shows the compact centrifugal valve enlarged. It consists of a switching piston 56 and a switching piston spring 57.
  • the switching piston 56 is aligned for spatial reasons obliquely to the radial centrifugal force direction, but could also be radially aligned in certain cases, i. its orientation must have at least one radial component.
  • the stepped receiving bore of the switching piston 56 and the switching piston spring 57 can partially protrude even for reasons of space in a tooth of the drive gear 55.
  • the position shown of the control piston 56 with a relaxed control piston spring 57 corresponds to low operating speeds with low centrifugal force.
  • a control pin 59 located on the control piston 56 ensures the radial guidance of the control piston spring 57 and prevents its centrifugal force-induced deflections.
  • the switching piston 56 shifts centrifugal force against the switching piston spring 57 in its outer end position.
  • the oil pressure increase to the second control pressure level of 5 bar of the stepped piston 51 relieved of pressure on its second effective surface 54 by a connection to the central bore 65 of the open-end drive shaft 58 is made via the oblique bore 61 and a circumferential groove 64 of the control piston 56 and other cross-sections ,
  • FIG. 5 shows an exemplary embodiment in which the stepped piston 51 can be acted upon with oil pressure at its second active surface 54 by two further independent control devices shown in FIG. 5.
  • the two control devices can, as shown in Fig. 5, both in combination with each other in function, but also each work for themselves in elimination of the other drive means.
  • the first drive means has on the drive shaft 74 a spiral groove 73 which is bounded on both sides by the circumferential grooves 75 and 76. It has a relatively small groove depth and generated upon rotation of the drive shaft 74 by occurring ⁇ lscher concept over its length a speed-dependent pressure gradient.
  • the left-side circumferential groove 75 is acted upon by the oil bore 27 with oil pressure.
  • the pitch direction of the spiral groove 73 is now selected so that upon rotation of the drive shaft 74, the pressure gradient acting in the spiral groove 73 causes a pressure reduction in the right-side circumferential groove 76.
  • the variable-speed pressure in the circumferential groove 76 is guided via a longitudinal bore of the drive shaft 74 and a connection bore 79 located in the housing 78 on the second effective surface 54 of stepped piston 51.
  • the second, alone or together with the first installable, drive means for the stepped piston 51 consists of an electric valve 71 which switches the oil pressure on the second effective surface 54 when electrically activated to the oil pressure reduction of the oil pump.
  • both active surfaces 53 and 54 are oil pressure loaded, so that the stepped piston 51 already exerts its control function, for example, at 2.5 bar oil pressure of the first control pressure stage against the force of the control spring 52 and provides the appropriate control pressure for flow control.
  • the oil pressure supply is interrupted and a pressure relief or load of the second effective surface 54 is produced via a discharge port 72 on the solenoid valve 71.
  • the now only on the first effective surface 53 of stepped piston 51 applied oil pressure shifts the start of control then to a higher value, for example, 5 bar, the second control pressure level.
  • the second control pressure stage is at a defect-related interruption of the electrical connections of the solenoid valve 71st guaranteed as safety oil pressure for all operating conditions of the internal combustion engine.
  • a continuously variable speed oil pressure control can be performed at operating warm combustion engine through the spiral groove 73, but the solenoid valve 71 must then keep its connection to the stepped piston 51 by an additional function.
  • the solenoid valve 71 When cold operation and then because of viscous oil effectively unusable effect of the spiral groove 73 then enters the solenoid valve 71 in operation.
  • Its two-stage oil pressure control by pressurization or pressure relief of the second effective surface 54 of the stepped piston 51 is then carried out in a known manner.
  • control of the oil pressure with the stepped piston 51 can also be carried out in several stages with a correspondingly designed graduated piston.
  • its part-active surfaces for example, would have to be subjected to a rotational speed offset by a multi-stage control device with oil pressure.
  • FIG. 6 shows an arrangement in which the stepping motor 29 is combined with the control piston 80 in a common housing 81 to form a control unit 82.
  • the externally mounted on the crankcase 84 control unit 82 ensures a trouble-free electrical connection 83 and a flange 85 penetrating the control bore 87 to the spring chamber 12 of the oil pump 86 a reliable oil pump pressure control.
  • control unit 82 is fed from an adjacent crankcase main oil hole 88 with purified oil filter 89 in pressurized oil.
  • This pressure oil is constantly relevant to regulation via corresponding connection cross sections of the control unit 82 end face on the effective surface 90 of the control piston 80 as well as a line 91 in the displacement chamber 28 of the oil pump 86.
  • a working in two control stages, electrically controlled control unit 100 is shown with an arrangement on the crankcase. It consists of the already described with reference to FIG. 5 step piston 51, an associated housing 101 and an electric valve 102.
  • the oil pump 103 is pressure-controlled only via the connecting control bore 87 in this two-stage pressure control.
  • the second active surface 54 of the stepped piston 51 is relieved of pressure via the left relief channel 92 in FIG. 7 so that the stepped piston 51 acted upon by the oil pressure only via the first effective surface 53 then executes the oil pump pressure control at a higher pressure control level with its control spring 52 ,
  • the second effective surface 54 of the stepped piston 51 is acted upon by the oil pressure, so that then the pressure control of the oil pump 103 is carried out at lowered pressure control level.
  • the control of the oil pressure according to the invention is largely independent of the temperature-dependent viscosity of the feed oil. This can be achieved by the proposed pressure control for oil pumps of motor vehicle internal combustion engines not only with warm engine, but especially in daily cold operation with low after an engine even low oil temperatures effectively reduced fuel consumption by not inconsiderably lowered oil pump drive services.

Claims (9)

  1. Dispositif pour la régulation de pression de pompes hydrauliques, en particulier pour des pompes à huile pour l'alimentation en huile de lubrification de moteurs à combustion, avec un dispositif de régulation du débit de refoulement et une unité à piston (8, 9) sollicitée par une pression d'huile, sur laquelle agissent - en s'opposant à la pression d'huile - un ressort de piston (11) ainsi qu'une pression de régulation, soutenant l'effet de ce ressort de piston (11), pour la commande du dispositif de régulation de débit de refoulement, caractérisé en ce que la pression de régulation est produite par un piston de régulation (14, 51, 80), présentant une surface active (15, 53, 80) pour une pression d'huile appliquée en permanence, un ressort de régulation (17, 52) agissant à l'encontre de la pression d'huile ainsi qu'un dispositif de commande (23, 29, 56, 71, 73, 102) avec une force additionnelle agissant sur le piston de régulation (14, 51, 80).
  2. Dispositif de régulation de pression de pompes hydrauliques selon la revendication 1, caractérisé en ce qu'au moins l'une des caractéristiques suivantes est prévue, concernant la réalisation du dispositif de commande :
    a) le dispositif de commande du piston de régulation (14, 80) est réalisé avec une bobine magnétique (23), comprenant un induit (24) agissant sur le piston de régulation (14, 80) ;
    b) le dispositif de commande du piston de régulation (14, 80) est réalisé avec un moteur pas à pas (29), pour régler l'appui élastique (30) du ressort de régulation (17) ;
    c) le dispositif de commande est réalisé avec une soupape centrifuge, dépendant de la vitesse de rotation, avec un piston de commutation (56) et un ressort de piston de commutation (57) ;
    d) le dispositif de commande est réalisé avec une électrovanne (71, 102) ;
    e) le dispositif de commande (23, 29, 71, 102) est réalisé de manière que, dans le cas d'une panne électrique du système, la pression d' huile augmente automatiquement au niveau de pression de régulation maximum ;
    f) le dispositif de commande est réalisé avec une rainure en spirale (73).
  3. Dispositif de régulation de pression de pompes hydrauliques selon l'une des revendications précédentes, caractérisé en ce que, concernant la réalisation du piston de régulation (14, 80), au moins l'une des caractéristiques suivantes est prévue :
    a) le piston de régulation est réalisé sous la forme de piston à étages (51) ayant une deuxième surface active (54), susceptible d'être sollicitée par, ou susceptible être déchargée d'une pression d'huile, par le dispositif de commande (56, 71, 73, 102) ;
    b) un piston de régulation à étages est réalisé avec plusieurs étages et est susceptible être sollicité par une pression d'huile, par un dispositif de commande réalisé de manière correspondante avec plusieurs étages.
  4. Dispositif de régulation de pression de pompes hydrauliques selon l'une des revendications précédentes, caractérisé en ce que le piston de commutation (56) présente, avec son axe, un décalage angulaire par rapport à la direction radiale de la force centrifuge.
  5. Dispositif de régulation de pression de pompes hydrauliques selon l'une des revendications précédentes, caractérisé en ce que le piston de commutation (56), ainsi qu'également le ressort de piston de commutation (57), sont disposés à l'intérieur d'une roue dentée de refoulement (55), avec une pénétration partielle dans une dent de refoulement.
  6. Dispositif de régulation de pression de pompes hydrauliques selon l'une des revendications précédentes, caractérisé en ce que le piston de commutation (56) présente un tourillon de guidage (59), servant au guidage radial du ressort de piston de commutation (57).
  7. Dispositif de régulation de pression de pompes hydrauliques selon l'une des revendications précédentes, caractérisé en ce que la pression d'huile, servant à la sollicitation en pression des surfaces actives (15, 53, 54, 90) du piston de régulation (14, 51, 80), est prélevée en aval d'un filtre à huile (25, 89).
  8. Dispositif de régulation de pression de pompes hydrauliques selon l'une des revendications précédentes, caractérisé en ce que des composants électriques de la régulation de pompes à huile (23, 29, 71, 82, 102) sont disposés à l'extérieur d'enceintes à huile et sont reliés à la pompe à huile (78, 86, 103) par des conduites hydrauliques (87, 91).
  9. Dispositif de régulation de pression de pompes hydrauliques selon l'une des revendications précédentes, caractérisé en ce que le piston de régulation (14, 80) est groupé, avec le moteur pas à pas (29), ou avec la bobine magnétique (23) et/ou l'électrovanne (102), dans un boîtier (81, 101) commun, pour former une unité de régulation (82, 100).
EP02806046A 2002-01-12 2002-12-09 Dispositif pour reguler la pression de pompes hydrauliques Revoked EP1463888B1 (fr)

Applications Claiming Priority (9)

Application Number Priority Date Filing Date Title
DE10200977 2002-01-12
DE10200977 2002-01-12
DE10223659 2002-05-28
DE10223659 2002-05-28
DE10230040 2002-07-04
DE10230040 2002-07-04
DE10237801A DE10237801C5 (de) 2002-01-12 2002-08-17 Vorrichtung zur Druckregelung von Hydraulikpumpen
DE10237801 2002-08-17
PCT/IB2002/005187 WO2003058071A1 (fr) 2002-01-12 2002-12-09 Dispositif pour reguler la pression de pompes hydrauliques

Publications (2)

Publication Number Publication Date
EP1463888A1 EP1463888A1 (fr) 2004-10-06
EP1463888B1 true EP1463888B1 (fr) 2006-05-17

Family

ID=27438038

Family Applications (1)

Application Number Title Priority Date Filing Date
EP02806046A Revoked EP1463888B1 (fr) 2002-01-12 2002-12-09 Dispositif pour reguler la pression de pompes hydrauliques

Country Status (7)

Country Link
US (1) US20050142006A1 (fr)
EP (1) EP1463888B1 (fr)
JP (1) JP4381816B2 (fr)
AT (1) ATE326633T1 (fr)
AU (1) AU2002367332A1 (fr)
DE (1) DE50206845D1 (fr)
WO (1) WO2003058071A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2066904B1 (fr) 2006-09-26 2017-03-22 Magna Powertrain Inc. Système et procédé de régulation pour réguler la pression de sortie d'une pompe

Families Citing this family (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2005057013A1 (fr) 2003-12-10 2005-06-23 Dieter Voigt Regulation de la pression de pompes a huile en fonction du regime du moteur
AT500629B8 (de) * 2004-05-27 2007-02-15 Tcg Unitech Ag Zahnradpumpe
FR2874645B1 (fr) * 2004-08-24 2006-12-01 Filtrauto Sa Systeme de pompage d'huile de lubrification
AT503856B1 (de) * 2006-06-30 2008-01-15 Tcg Unitech Systemtechnik Gmbh Zahnradpumpe mit veränderbarem fördervolumen
KR100783883B1 (ko) * 2006-12-14 2007-12-10 현대자동차주식회사 엔진의 메인 갤러리 압력조절장치
DE102007033146B4 (de) 2007-07-13 2012-02-02 Schwäbische Hüttenwerke Automotive GmbH & Co. KG Verstellventil für die Verstellung des Fördervolumens einer Verdrängerpumpe
US8511274B2 (en) 2007-10-31 2013-08-20 Caterpillar Inc. Engine speed sensitive oil pressure regulator
DE102010020356A1 (de) * 2010-05-12 2011-11-17 Audi Ag Schmiermittelpumpe, Regelkolben
JP5614142B2 (ja) * 2010-05-26 2014-10-29 トヨタ自動車株式会社 車載潤滑油供給装置
JP6029878B2 (ja) * 2012-07-06 2016-11-24 株式会社山田製作所 制御バルブ
JP5922511B2 (ja) * 2012-07-06 2016-05-24 株式会社山田製作所 制御バルブ
DE102015109156B4 (de) 2015-06-10 2019-11-07 Schwäbische Hüttenwerke Automotive GmbH Pumpe mit Verstelleinrichtung und Steuerventil zur Verstellung des Fördervolumens der Pumpe

Family Cites Families (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4275607A (en) * 1979-06-28 1981-06-30 Twin Disc, Incorporated Power transmission having power take-off shaft and fluid control means therefor
DE3528651A1 (de) * 1985-08-09 1987-02-19 Rohs Hans Guenther Prof Dr Ing Zahnradpumpe
DE3824398C2 (de) * 1987-07-23 1993-11-18 Barmag Barmer Maschf Schmierölpumpe
US4828462A (en) * 1987-12-10 1989-05-09 Dana Corporation Pressure detecting system for a hydraulic device
DE4038549C1 (en) * 1990-12-04 1992-01-09 Mercedes-Benz Aktiengesellschaft, 7000 Stuttgart, De IC engine oil pressure regulator - has piston control chamber connected to oil circuit pump assembly
FR2673676A1 (fr) * 1991-03-06 1992-09-11 Renault Procede de lubrification a carter sec pour moteur a combustion interne et dispositif pour sa mise en óoeuvre.
US5569110A (en) * 1991-10-10 1996-10-29 Warren; Walter S. Integrated hydro-mechanical automobile transmission
US5842420A (en) * 1992-09-07 1998-12-01 Khoo; Chew Thong Crankshaft lubrication system
JPH0814164A (ja) * 1994-06-28 1996-01-16 Unisia Jecs Corp 内接型オイルポンプ
DE4444819A1 (de) * 1994-12-15 1996-06-20 Bayerische Motoren Werke Ag Schmierölpumpe einer Brennkraftmaschine
US6244839B1 (en) * 1997-11-14 2001-06-12 University Of Arkansas Pressure compensated variable displacement internal gear pumps
US5921279A (en) * 1998-04-29 1999-07-13 Husco International, Inc. Solenoid operated dual spool control valve
DE50113387D1 (de) * 2000-03-02 2008-01-31 Volkswagen Ag Zahnradpumpe mit einer fördermengenverändernden Verschiebeeinheit
WO2002016739A2 (fr) * 2000-08-21 2002-02-28 Bombardier-Rotax Gmbh & Co. Kg. Systeme de commande de turbocompresseur et systeme de commande d'helice mettant en oeuvre un moteur pas a pas

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2066904B1 (fr) 2006-09-26 2017-03-22 Magna Powertrain Inc. Système et procédé de régulation pour réguler la pression de sortie d'une pompe

Also Published As

Publication number Publication date
AU2002367332A1 (en) 2003-07-24
JP4381816B2 (ja) 2009-12-09
ATE326633T1 (de) 2006-06-15
US20050142006A1 (en) 2005-06-30
DE50206845D1 (de) 2006-06-22
EP1463888A1 (fr) 2004-10-06
WO2003058071A1 (fr) 2003-07-17
JP2005526204A (ja) 2005-09-02

Similar Documents

Publication Publication Date Title
DE10237801B4 (de) Vorrichtung zur Druckregelung von Hydraulikpumpen
DE112007002915B4 (de) Verstelleinrichtung zur Phaseneinstellung einer Nockenwelle
DE10220305B4 (de) Anordnung zum variablen Pumpen von Drucköl und Schmiereinrichtung
EP2427674B1 (fr) Dispositif de chaîne cinématique
EP2014919B2 (fr) Soupape de réglage pour le réglage du volume d'alimentation d'une pompe volumétrique
EP1463888B1 (fr) Dispositif pour reguler la pression de pompes hydrauliques
DE112008000978T5 (de) Hydraulische Pumpe mit variablem Durchfluss und Druck und verbesserter elektrischer Steuerung mit offenem Regelkreis
DE102007039589A1 (de) Regelölpumpe mit verstellwegabhängiger Öldruckregelung
EP3371423B1 (fr) Dispositif de refoulement pour le refoulement d'huile
EP0533720B1 (fr) Dispositif d'entrainement
DE3622335C2 (de) Antriebseinrichtung für Nebenaggregate einer Brennkraftmaschine
DE10043842A1 (de) Zahnradpumpe mit einer fördermengenverändernden Verschiebeeinheit
WO2020120064A1 (fr) Pompe à broche hélicoïdale régulable
DE3824398C2 (de) Schmierölpumpe
DE19908146B4 (de) Vorrichtung zum Verändern der Steuerzeiten von Gaswechselventilen einer Brennkraftmaschine
EP1130262B1 (fr) Pompe à engrenages avec dispositif glissant pour changer le débit
DE60220337T2 (de) Hydraulisches Steuergerät
WO2005057013A1 (fr) Regulation de la pression de pompes a huile en fonction du regime du moteur
EP3292282B1 (fr) Dispositif de régulation de la pression d'une pompe à huile
DE3943299A1 (de) Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
DE102009060189B4 (de) Regelvorrichtung für die Verstellung des Fördervolumens einer Pumpe
EP0259619B1 (fr) Pompe à huile de lubrification
EP3848592A1 (fr) Système d'alimentation en liquide destiné à l'alimentation de plusieurs consommateurs de fluide d'un véhicule automobile en fluide
DE10051780A1 (de) Druckregeleinheit für einen Ölkreislauf eines Kraftfahrzeugverbrennungsmotors
DE10023330C1 (de) Regelbare Pumpe

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

17P Request for examination filed

Effective date: 20040617

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR IE IT LI LU MC NL PT SE SI SK TR

AX Request for extension of the european patent

Extension state: AL LT LV MK RO

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR IE IT LI LU MC NL PT SE SI SK TR

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

Ref country code: CZ

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20060517

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20060517

Ref country code: SI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20060517

Ref country code: NL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20060517

Ref country code: IE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20060517

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20060517

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Free format text: LANGUAGE OF EP DOCUMENT: GERMAN

REF Corresponds to:

Ref document number: 50206845

Country of ref document: DE

Date of ref document: 20060622

Kind code of ref document: P

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

Effective date: 20060628

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

Ref country code: SE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20060817

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20060817

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

Ref country code: ES

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20060828

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

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20061017

NLV1 Nl: lapsed or annulled due to failure to fulfill the requirements of art. 29p and 29m of the patents act
ET Fr: translation filed
REG Reference to a national code

Ref country code: IE

Ref legal event code: FD4D

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

Ref country code: MC

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

Effective date: 20061231

Ref country code: CH

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

Effective date: 20061231

Ref country code: BE

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

Effective date: 20061231

Ref country code: LI

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

Effective date: 20061231

PLBI Opposition filed

Free format text: ORIGINAL CODE: 0009260

PLAX Notice of opposition and request to file observation + time limit sent

Free format text: ORIGINAL CODE: EPIDOSNOBS2

26 Opposition filed

Opponent name: SCHWAEBISCHE HUETTENWERKE AUTOMOTIVE GMBH & CO. KG

Effective date: 20070216

PLBB Reply of patent proprietor to notice(s) of opposition received

Free format text: ORIGINAL CODE: EPIDOSNOBS3

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: 20070703

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

BERE Be: lapsed

Owner name: VOIGT, DIETER, DIPL.-ING.

Effective date: 20061231

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

Ref country code: AT

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

Effective date: 20061209

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

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20060818

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

Ref country code: EE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20060517

Ref country code: BG

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20060817

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

Ref country code: LU

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

Effective date: 20061209

Ref country code: TR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20060517

PLAB Opposition data, opponent's data or that of the opponent's representative modified

Free format text: ORIGINAL CODE: 0009299OPPO

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

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20060517

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

Ref country code: FR

Payment date: 20101221

Year of fee payment: 9

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

Ref country code: IT

Payment date: 20101223

Year of fee payment: 9

Ref country code: GB

Payment date: 20101220

Year of fee payment: 9

PLAY Examination report in opposition despatched + time limit

Free format text: ORIGINAL CODE: EPIDOSNORE2

PLAH Information related to despatch of examination report in opposition + time limit modified

Free format text: ORIGINAL CODE: EPIDOSCORE2

RDAD Information modified related to despatch of communication that patent is revoked

Free format text: ORIGINAL CODE: EPIDOSCREV1

RDAF Communication despatched that patent is revoked

Free format text: ORIGINAL CODE: EPIDOSNREV1

PLBC Reply to examination report in opposition received

Free format text: ORIGINAL CODE: EPIDOSNORE3

RDAG Patent revoked

Free format text: ORIGINAL CODE: 0009271

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

Free format text: STATUS: PATENT REVOKED

27W Patent revoked

Effective date: 20120103

GBPR Gb: patent revoked under art. 102 of the ep convention designating the uk as contracting state

Effective date: 20120103