EP2440785B1 - Schmierstoffpumpensystem - Google Patents

Schmierstoffpumpensystem Download PDF

Info

Publication number
EP2440785B1
EP2440785B1 EP10724493.1A EP10724493A EP2440785B1 EP 2440785 B1 EP2440785 B1 EP 2440785B1 EP 10724493 A EP10724493 A EP 10724493A EP 2440785 B1 EP2440785 B1 EP 2440785B1
Authority
EP
European Patent Office
Prior art keywords
lubricant pump
lubricant
pressure
proportional valve
internal combustion
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP10724493.1A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP2440785A1 (de
Inventor
René Wagner
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.)
Mahle International GmbH
Original Assignee
Mahle International GmbH
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
Priority claimed from DE200910024698 external-priority patent/DE102009024698A1/de
Priority claimed from DE102009048320A external-priority patent/DE102009048320A1/de
Application filed by Mahle International GmbH filed Critical Mahle International GmbH
Publication of EP2440785A1 publication Critical patent/EP2440785A1/de
Application granted granted Critical
Publication of EP2440785B1 publication Critical patent/EP2440785B1/de
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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
    • F04C14/22—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members
    • F04C14/223—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members using a movable cam
    • F04C14/226—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members using a movable cam by pivoting the cam around an eccentric axis
    • 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
    • F04C14/22—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members
    • F04C14/223—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members using a movable cam
    • 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
    • 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
    • F04C14/28—Safety arrangements; Monitoring
    • 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
    • F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C2/32—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having both the movement defined in groups F04C2/02 and relative reciprocation between co-operating members
    • F04C2/332—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having both the movement defined in groups F04C2/02 and relative reciprocation between co-operating members with vanes hinged to the outer member and reciprocating with respect to the inner member
    • 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
    • F04C2270/18—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
    • F04C2270/24—Level of liquid, e.g. lubricant or cooling liquid
    • 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
    • F04C2270/70—Safety, emergency conditions or requirements

Definitions

  • the present invention relates to a map-controlled lubricant pump system with a lubricant pump for supplying an internal combustion engine with lubricant.
  • the invention also relates to a lubricant pump for such a map-controlled lubricant pump system.
  • WO 2008/037070 A1 is a map-controlled lubricant pump system with a lubricant pump, in particular a cell pump, known for supplying an internal combustion engine with lubricant.
  • the lubricant pump is controlled by a proportional valve, which is connected on the input side to the internal combustion engine.
  • a proportional valve which is connected on the input side to the internal combustion engine.
  • a biased by a spring adjusting unit is arranged, via which a delivery rate of the lubricant pump is controlled.
  • On the adjusting unit acts a first pressure chamber, which is also arranged in the lubricant pump and can be acted upon with pressure and thereby adjusts the adjusting unit against the spring and which the proportional valve is connected upstream.
  • volume-controlled lubricant pumps in internal combustion engines is state of the art, for example, to be able to approximate a flow rate and a pressure to the needs of the respective needs of the internal combustion engine. This is usually done by applying an actuating unit within the lubricant pump, such as a control piston or a collar, with an originating from a Hauptöl mode the engine oil pressure.
  • an actuating unit within the lubricant pump such as a control piston or a collar
  • the disadvantage of such a control is that the control is in direct connection of the pressure prevailing in the engine oil pressure, the flow rate, an engine speed, a lubricant temperature and a voltage applied to the actuator spring force.
  • characteristic map controls is the decoupling of said direct influencing variables on the control in order to achieve a control map of the lubricant pump, which can respond to each individual influencing variable, thus coming closer to the needs of the internal combustion engine and at least reduce further drive and power losses.
  • proportional valves are used which switch on or off a control oil pressure from the main oil gallery or from an outlet of the lubricant pump as needed to the actuators.
  • the lubricant pump gets no Abregeltik on the proportional valve and thus promotes the maximum possible flow in the main oil gallery of the engine.
  • the second-level valve is acted upon only on one side by the increasing lubricant pressure of the main oil gallery and at the same time assumes a position in which the lubricant, ie the oil, of the main oil gallery can flow in and out of the actuating unit as a function of the oil pressure and thus regulates the lubricant pump to a desired higher pressure level.
  • a disadvantage of such a lubricant supply system is a high number of parts with associated high assembly, storage and logistics costs.
  • the present invention is concerned with the problem of providing a map-controlled lubricant pump system, which operates reliably and at the same time is inexpensive to implement.
  • the present invention is based on the general idea of eliminating a previously conventional "second-level valve" by a corresponding design of a lubricant pump in a map-controlled lubricant pump system with a lubricant pump.
  • map-controlled lubricant pump system of the actual lubricant pump is preceded by a proportional valve, which is the input side connected to the internal combustion engine and / or communicating with an output of the lubricant pump.
  • a proportional valve which is the input side connected to the internal combustion engine and / or communicating with an output of the lubricant pump.
  • a spring-biased actuating unit for example a ring or a slide, is arranged, via which a delivery rate of the lubricant pump, which is usually designed as a cell pump, can be regulated.
  • the lubricant pump according to the invention has a first pressure chamber acting on the setting unit, which can be acted upon by pressure under characteristic map control and thereby displaces the setting unit against the spring and at least two second pressure chambers acting in the same way on the setting unit.
  • the second pressure chambers are dimensioned smaller than the first, so that in case of failure of the proportional valve, the lubricant pump is pressurized exclusively via the at least two second pressure chambers and due to their smaller dimension, a higher lubricant pressure, that is, a higher oil pressure generated, so that the internal combustion engine is supplied with lubricant at a higher pressure level when the proportional valve fails.
  • a permanently applied lubricant pressure acts on the first pressure chamber, as well as on the two second pressure chambers, wherein the ratio of the two pressure chambers and the spring biasing the actuator is designed so that the permanently applied lubricant pressure and the supplied via the proportional valve lubricant pressure the complete Map covers.
  • the two second permanently impinged pressure chambers are dimensioned so that in case of failure of the proportional valve, so the sole concern of the permanent lubricant pressure at the second pressure chambers, the lubricant pump due to the constant spring counterforce on the actuator continues to operate at a higher pressure level and the internal combustion engine Lubricant, that is supplied in particular with oil.
  • the lubricant pump system according to the invention thus has a lower variety of parts and associated lower storage and logistics costs and lower installation costs.
  • eliminating the second-level valve eliminates interactions with the actuator.
  • the map-controlled lubricant pump system according to the invention works in case of failure of the proportional valve at a higher balance of forces, which minimizes the influence of internal forces from a pump running set.
  • the lubricant pump according to the invention can also be used elsewhere, so that the lubricant pump system according to the invention relates to a map control of all hydraulically variably controllable lubricant pumps for internal combustion engines with second-level control.
  • the factors such as lubricant pressure, volume flow, engine speed, lubricant temperature and the spring force applied to the actuator can be taken into account separately.
  • Map-controlled means that, contrary to the two-stage or multi-stage control, the proportional valve is not "only” added or disconnected, and thus the additional pressure or control chamber is subjected to control pressure.
  • the temperature, the speed, the oil pressure, the load case, etc. of the unit to be supplied, for example, an internal combustion engine determined and compared with a predetermined map (control system).
  • the proportional valve is frequency-modulated controlled (uppulled) and placed on the basis of the respective position of the proportional valve, the actuating unit of the lubricant pump in a certain position, that of the lubricant pump allows the flow rate and discharge pressure to be displayed according to the given "characteristic field".
  • the control pressures in direct dependence on oil temperature (medium temperature), speed u. the given geometries of the (pressure) chambers. Here only the pressure chambers are added.
  • the lubricant pump according to the invention is continuously supplied with control pressure which corresponds to the SLR level.
  • One advantage is that the lubricant pump can be controlled with pump output pressure (controlled internally) or with the pressure from the main supply channel and any points in the supply circuit.
  • the map control system controls the proportional valve at high frequency and due to the respective position of the proportional valve, another actuating range is provided with pressure to the already existing SLR pressure range and brought the adjustment of the lubricant pump in a certain position, which allows the lubricant pump, flow rate and discharge pressure to represent the given "map".
  • Fig. 1 has a map-controlled lubricant pump system 1, a lubricant pump 2, which is for example designed as a cell pump, and which serves to supply an internal combustion engine 3 with lubricant.
  • a filter 4 connected to an output side of the lubricant pump 2
  • a pressure sensor 5 and a proportional valve 6 are also arranged, the latter for example as a 3/2-way valve can be trained.
  • the lubricant pump system 1 according to the invention also includes a lubricant reservoir 7 in which the lubricant, for example the oil 8, is collected. Regardless of whether oil 8 is mentioned below, this naturally also includes any other common lubricant.
  • an adjustable adjusting unit 9 is arranged, via which a delivery rate of the lubricant pump 2 is controlled, and which is biased by a spring 10.
  • an oil pressure acts which acts via a first pressure chamber 11 acting on the setting unit 9 as well as via at least two second pressure chambers 12, 12 '.
  • the lubricant pump 2 is pressurized exclusively via the second pressure chambers 12, 12 ', wherein due to the smaller dimensions of the second pressure chambers 12, 12', a higher lubricant pressure is generated, so that the internal combustion engine 3 even in the event of failure Proportional valve 6 on the one hand sufficiently supplied with lubricant, on the other hand, however, takes place at a relatively higher pressure level.
  • the actuator 9 is pivotally configured while, according to the Fig. 3 is designed as a translationally adjustable slider. Due to the map-controlled lubricant pump system 1 according to the invention, a hitherto required "second-level valve" can be dispensed with, as a result of which fewer parts are produced and mounted and thus the entire lubricant pump system 1 can be made more cost-effective. In addition, interactions of the now omitted second-level valve can be excluded with the actuator 9, wherein the lubricant pump system 1 according to the invention also in its second-level control, in which only the second pressure chambers 12, 12 'are pressurized, on a higher balance of forces works, which minimizes the influence of internal forces from a pump running set.
  • the proportional valve 6 serving to control the lubricant pump 2 in the normal operating state is connected on the input side via a main oil gallery to the internal combustion engine 3 or to the outlet of the lubricant pump 2.
  • a lubricant pump 1 a has a shaft 2 a, on which a rotor 3 a is arranged rotationally fixed.
  • the rotor 3a is operatively connected via a single pendulum 4a with a cage 5a, wherein the cage 5a is guided in a slide 6a.
  • the slider 6a in turn is pivotally mounted about a bearing pin 7a and biased by a spring 8a.
  • the spring 8a for example a control spring, is supported at one end on the slide 6a and at the other end against a spring counterpart 9a on the housing 10a of the lubricant pump 1a.
  • a capacity of the lubricant pump 1a according to the invention can be regulated, for example, by changing the volumes of a pressure chamber 11a and a suction chamber 12a by changing the eccentricity of the rotor 3a to the slider 6a.
  • the lubricant pump 1a is designed as a so-called cell pump and is usually used to supply an internal combustion engine, not shown, with lubricant, in particular with oil.
  • An adjustment of the slide 6a is effected by means of a hydraulic pressure within a control pressure chamber 14a, wherein an increase in the pressure in the control pressure chamber 14a causes an adjustment of the slide 6a against the spring 8a.
  • the slide 6a still separates a damping chamber 13a from a suction chamber 17a, wherein a separation between the control pressure chamber 14a, the damping chamber 13a and the suction chamber 17a via arranged on the slide 6 sealing strips 15a and 15a ', which the slider 6a relative to the housing 10a the lubricant pump 1 a seal.
  • connection 16a for example a connecting channel, to compensate for pressure fluctuations and thus to Damping of the lubricant pump 1 a provided.
  • the connection 16a can not only be designed as a connecting channel formed in the housing 10a, but also be integrated as a channel in the manner of a fingerschliff or already in the cast housing, between the slide 6a and the housing 10a.
  • the connection 16a is according to the Fig. 1 shown greatly enlarged so that it is usually designed so small that it unfolds a throttle effect.
  • connection 16a may also be provided between the damping chamber 13a and the suction chamber 17a, this connection 16a' extending within the slide 6a and, in this case, also being designed as a connecting channel.
  • a connection between the damping chamber 13a and the suction chamber 17a may alternatively be formed as a clearance between the slider 6a and the housing 10a, overcoming the sealing strip 15a '.
  • control pressure chamber 14a is usually smaller than the damping chamber 13a and is at the same time usually connected on the input side to a main oil gallery of the internal combustion engine.
  • a further alternative is to connect a damping volume (lubricant reservoir 18a) mounted outside the housing 10a to one of the volumes in the pump by means of a throttle bore acting like the connection 16a, 16a '.
  • connection 16a an overpumping of the oil is achieved from one to the other volume in all embodiments, at the same time there is a throttling whereby the pressure pulsations are reduced.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Lubrication Of Internal Combustion Engines (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
EP10724493.1A 2009-06-12 2010-06-04 Schmierstoffpumpensystem Active EP2440785B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE200910024698 DE102009024698A1 (de) 2009-06-12 2009-06-12 Schmierstoffpumpensystem
DE102009048320A DE102009048320A1 (de) 2009-10-05 2009-10-05 Schmierstoffpumpe
PCT/EP2010/057836 WO2010142611A1 (de) 2009-06-12 2010-06-04 Schmierstoffpumpensystem

Publications (2)

Publication Number Publication Date
EP2440785A1 EP2440785A1 (de) 2012-04-18
EP2440785B1 true EP2440785B1 (de) 2014-01-08

Family

ID=42561077

Family Applications (1)

Application Number Title Priority Date Filing Date
EP10724493.1A Active EP2440785B1 (de) 2009-06-12 2010-06-04 Schmierstoffpumpensystem

Country Status (6)

Country Link
US (1) US8992184B2 (zh)
EP (1) EP2440785B1 (zh)
JP (1) JP5589068B2 (zh)
KR (1) KR101753419B1 (zh)
CN (1) CN102459904B (zh)
WO (1) WO2010142611A1 (zh)

Families Citing this family (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102010023068A1 (de) * 2010-06-08 2011-12-08 Mahle International Gmbh Flügelzellenpumpe
DE102011004970A1 (de) * 2011-03-02 2012-09-06 Mahle International Gmbh Flügelzellenpumpe
DE102011083278A1 (de) * 2011-09-23 2013-03-28 Mahle International Gmbh Schmiermittelsystem
DE102011086175B3 (de) 2011-11-11 2013-05-16 Schwäbische Hüttenwerke Automotive GmbH Rotationspumpe mit verbesserter Abdichtung
DE102012210899A1 (de) * 2012-06-26 2014-01-02 Mahle International Gmbh Hydraulikfördereinrichtung und Hydrauliksystem
US9347344B2 (en) 2012-09-07 2016-05-24 Hitachi Automotive Systems, Ltd. Variable-capacity oil pump and oil supply system using same
JP6088313B2 (ja) * 2013-03-28 2017-03-01 本田技研工業株式会社 可変容量型オイルポンプ
JP2015140670A (ja) * 2014-01-27 2015-08-03 トヨタ自動車株式会社 可変容量形オイルポンプ
JP6270684B2 (ja) * 2014-10-03 2018-01-31 トヨタ自動車株式会社 油圧制御装置
WO2016059492A1 (en) * 2014-10-15 2016-04-21 Vhit S.P.A. Control system for controlling a positive displacement pump
US10030656B2 (en) * 2014-12-31 2018-07-24 Stackpole International Engineered Products, Ltd. Variable displacement vane pump with integrated fail safe function
DE102015101490B4 (de) 2015-02-02 2018-09-13 Schwäbische Hüttenwerke Automotive GmbH Verdrängerpumpe mit einem oder mehreren Sintermetallteilen
JP6616129B2 (ja) 2015-08-28 2019-12-04 株式会社マーレ フィルターシステムズ 可変容量ポンプ
JP2017048681A (ja) * 2015-08-31 2017-03-09 株式会社マーレ フィルターシステムズ ポンプ
DE102016108944A1 (de) * 2016-05-13 2017-11-16 Joma-Polytec Gmbh Verstellbare Flügelzellenpumpe
US11674455B2 (en) * 2021-03-26 2023-06-13 Hamilton Sundstrand Corporation Variable displacement pump with active bypass feedback control
CN114110398B (zh) * 2021-11-30 2023-03-24 湖南机油泵股份有限公司 一种能减小压力波动的变量机油泵

Family Cites Families (22)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS53130505A (en) * 1977-04-20 1978-11-14 Jidosha Kiki Co Ltd Variable capacity pump
DE3122598C1 (de) 1981-06-06 1983-01-27 Zahnradfabrik Friedrichshafen Ag, 7990 Friedrichshafen Regelbare Fluegelzellenpumpe
US4600364A (en) * 1983-06-20 1986-07-15 Kabushiki Kaisha Komatsu Seisakusho Fluid operated pump displacement control system
GB8417148D0 (en) * 1984-07-05 1984-08-08 Hobourn Eaton Ltd Variable capacity roller-and vane-type pumps
DE4231690A1 (de) 1992-09-22 1994-03-24 Walter Schopf Innenzahnradpumpe mit variierbarer Förderleistung
EP0851123B1 (de) 1996-12-23 2003-07-09 LuK Fahrzeug-Hydraulik GmbH & Co. KG Flügelzellenmaschine, insbesondere Flügelzellenpumpe
JP3866410B2 (ja) 1998-04-23 2007-01-10 ユニシア ジェーケーシー ステアリングシステム株式会社 可変容量形ポンプ
JP3847052B2 (ja) * 2000-03-31 2006-11-15 本田技研工業株式会社 内燃機関の燃料噴射制御装置
CN2436689Y (zh) 2000-06-08 2001-06-27 崔勇达 高性能双作用液压叶片泵
GB2372583A (en) * 2001-02-21 2002-08-28 Delphi Tech Inc High pressure fuel injected engine limp home control system
CA2565179C (en) 2004-05-07 2014-01-21 Magna Powertrain Inc. Vane pump using line pressure to directly regulate displacement
ITTO20050543A1 (it) * 2005-08-02 2007-02-03 Pierburg Spa Pompa a palette ad eccentricita' variabile con doppia regolazione
DE102005050216B4 (de) 2005-10-20 2014-01-09 Zf Lenksysteme Gmbh Volumenstromgeregelte, einhubige Flügelzellenpumpe
US20070224067A1 (en) 2006-03-27 2007-09-27 Manfred Arnold Variable displacement sliding vane pump
US8057201B2 (en) 2006-05-04 2011-11-15 Magna Powertrain Inc. Variable displacement vane pump with dual control chambers
EP2059680A4 (en) * 2006-09-08 2014-04-09 Slw Automotive Inc TWO-STAGE PRESSURE CONTROL SYSTEM FOR VARIABLE DISPLACEMENT HYDRAULIC PUMPS
CA2663123C (en) 2006-09-26 2016-10-25 Magna Powertrain Inc. Control system and method for pump output pressure control
DE102006061326B4 (de) 2006-12-22 2012-02-16 Mahle International Gmbh Stelleneinrichtung für eine mengenregelbare Zellenpumpe
US7862306B2 (en) 2007-02-06 2011-01-04 Gm Global Technology Operations, Inc. Pressure regulating variable displacement vane pump
JP2009036137A (ja) 2007-08-03 2009-02-19 Hitachi Ltd 可変容量型ベーンポンプ
JP2009047041A (ja) 2007-08-17 2009-03-05 Hitachi Ltd 可変容量型ベーンポンプ
JP5174720B2 (ja) * 2009-03-09 2013-04-03 日立オートモティブシステムズ株式会社 可変容量形ポンプ

Also Published As

Publication number Publication date
US20120148423A1 (en) 2012-06-14
JP2012529589A (ja) 2012-11-22
CN102459904A (zh) 2012-05-16
US8992184B2 (en) 2015-03-31
EP2440785A1 (de) 2012-04-18
CN102459904B (zh) 2015-04-01
JP5589068B2 (ja) 2014-09-10
KR20120027038A (ko) 2012-03-20
KR101753419B1 (ko) 2017-07-03
WO2010142611A1 (de) 2010-12-16

Similar Documents

Publication Publication Date Title
EP2440785B1 (de) Schmierstoffpumpensystem
EP1853824B1 (de) Vorrichtung und verfahren zur schmierölversorgung
DE112007001131B4 (de) Kontinuierlich verstellbare Drehschieberpumpe und entsprechendes System
EP1537335B1 (de) Einrichtung zur regelung der pumpleistung einer schmiermittelpumpe für eine brennkraftmaschine
DE10237801C5 (de) Vorrichtung zur Druckregelung von Hydraulikpumpen
EP1668282B1 (de) Druck-einspeiseventil
EP2307726B1 (de) Verstellpumpe mit einem mengenregler und einem druckventil.
EP3059437B1 (de) Pumpeneinheit für eine hochdruckpumpe
DE102007039589A1 (de) Regelölpumpe mit verstellwegabhängiger Öldruckregelung
WO2012149929A2 (de) Verstellpumpe
DE112015001797T5 (de) Verstellpumpe mit hydraulikdurchgang
EP2049800B1 (de) Förderpumpe
DE102009023824A1 (de) Thermostat-Druckbegrenzungsventil, selbstregelnde Fluidpumpe und Schmierölkreislauf einer Brennkraftmaschine
DE102009005768B4 (de) Druckregelung einer hydraulischen Antriebseinheit
WO2013037481A1 (de) Hochdruckpumpensystem
DE60305812T2 (de) Hydraulische Pumpe mit doppeltem Auslass und System mit derselben
EP3877676B1 (de) Systemdruckventil für ein hydrauliksystem eines kraftfahrzeug-getriebes
DE102020125021A1 (de) Reihenkolbenpumpe
DE102015204040A1 (de) Nockenwellenversteller
DE102009024698A1 (de) Schmierstoffpumpensystem
DE102004054108A1 (de) Dreiwegeventil und dieses aufweisende Brennstoffeinspritzvorrichtung
DE202006015508U1 (de) Förderpumpe
DE10023330C1 (de) Regelbare Pumpe
DE10234621A1 (de) Regeleinrichtung für eine Verstellpumpe, insbesondere eine Flügelzellenpumpe
DE19827970A1 (de) Regeleinrichtung für Hydraulikpumpen

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: 20111207

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO SE SI SK SM TR

DAX Request for extension of the european patent (deleted)
17Q First examination report despatched

Effective date: 20130214

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

INTG Intention to grant announced

Effective date: 20130819

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): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO SE SI SK SM TR

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

REG Reference to a national code

Ref country code: AT

Ref legal event code: REF

Ref document number: 648927

Country of ref document: AT

Kind code of ref document: T

Effective date: 20140215

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 502010005898

Country of ref document: DE

Effective date: 20140220

REG Reference to a national code

Ref country code: NL

Ref legal event code: VDEP

Effective date: 20140108

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG4D

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

Ref country code: IS

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: 20140508

Ref country code: NO

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: 20140408

Ref country code: LT

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: 20140108

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

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: 20140108

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: 20140108

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: 20140108

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: 20140508

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: 20140108

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: 20140108

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

Ref country code: LV

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: 20140108

Ref country code: HR

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: 20140108

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 502010005898

Country of ref document: DE

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: 20140108

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: 20140108

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: 20140108

Ref country code: RO

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: 20140108

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

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

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: 20140108

Ref country code: PL

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: 20140108

26N No opposition filed

Effective date: 20141009

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 502010005898

Country of ref document: DE

Effective date: 20141009

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 FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20140108

Ref country code: LU

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: 20140604

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

REG Reference to a national code

Ref country code: IE

Ref legal event code: MM4A

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

Ref country code: CH

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

Effective date: 20140630

Ref country code: IE

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

Effective date: 20140604

Ref country code: LI

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

Effective date: 20140630

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

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: 20140108

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

Ref country code: MT

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: 20140108

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

Ref country code: SM

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: 20140108

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: 20140409

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: 20140108

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 7

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

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: 20140108

Ref country code: BE

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: 20140630

Ref country code: HU

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

Effective date: 20100604

REG Reference to a national code

Ref country code: AT

Ref legal event code: MM01

Ref document number: 648927

Country of ref document: AT

Kind code of ref document: T

Effective date: 20150604

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: 20150604

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 8

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

Ref country code: MK

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: 20140108

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 9

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

Ref country code: AL

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: 20140108

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

Ref country code: FR

Payment date: 20200626

Year of fee payment: 11

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

Ref country code: GB

Payment date: 20200630

Year of fee payment: 11

Ref country code: IT

Payment date: 20200618

Year of fee payment: 11

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

Effective date: 20210604

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: 20210604

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: 20210630

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: 20210604

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

Ref country code: DE

Payment date: 20230620

Year of fee payment: 14