EP0681656B1 - Procede de regulation de la capacite de pompage de pompes a lubrifiant et pompe a lubrifiant appropriee - Google Patents
Procede de regulation de la capacite de pompage de pompes a lubrifiant et pompe a lubrifiant appropriee Download PDFInfo
- Publication number
- EP0681656B1 EP0681656B1 EP94905653A EP94905653A EP0681656B1 EP 0681656 B1 EP0681656 B1 EP 0681656B1 EP 94905653 A EP94905653 A EP 94905653A EP 94905653 A EP94905653 A EP 94905653A EP 0681656 B1 EP0681656 B1 EP 0681656B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- pump
- pressure
- temperature
- lubricant
- control
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Lifetime
Links
- 239000000314 lubricant Substances 0.000 title claims abstract description 54
- 238000000034 method Methods 0.000 title claims abstract description 10
- 230000001105 regulatory effect Effects 0.000 title abstract description 10
- 230000001419 dependent effect Effects 0.000 claims description 10
- 230000001276 controlling effect Effects 0.000 abstract description 2
- 239000003921 oil Substances 0.000 description 42
- 238000002485 combustion reaction Methods 0.000 description 8
- 230000007423 decrease Effects 0.000 description 5
- 238000005461 lubrication Methods 0.000 description 5
- 230000033228 biological regulation Effects 0.000 description 4
- 230000008901 benefit Effects 0.000 description 3
- 230000006835 compression Effects 0.000 description 2
- 238000007906 compression Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 229910052751 metal Inorganic materials 0.000 description 2
- 230000009467 reduction Effects 0.000 description 2
- 238000011144 upstream manufacturing Methods 0.000 description 2
- 230000009471 action Effects 0.000 description 1
- 230000004913 activation Effects 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 230000003247 decreasing effect Effects 0.000 description 1
- 238000001514 detection method Methods 0.000 description 1
- 238000005265 energy consumption Methods 0.000 description 1
- 239000010687 lubricating oil Substances 0.000 description 1
- 238000005259 measurement Methods 0.000 description 1
- 239000002184 metal Substances 0.000 description 1
- 239000010705 motor oil Substances 0.000 description 1
- 230000036316 preload Effects 0.000 description 1
- 230000009747 swallowing Effects 0.000 description 1
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
- F04C2270/00—Control; Monitoring or safety arrangements
- F04C2270/19—Temperature
Definitions
- the present invention relates to a method for regulating the Pump performance of lubricant pumps, in which the pump performance over the prevailing at the pump outlet or at a consumption point Pressure is controlled so that the pressure increases Pump power is effectively reduced.
- the present concerns Invention a controllable lubricant pump with a Control device through which to limit the flow rate Pump power is effectively reduced.
- a corresponding procedure and a corresponding device are from DE 33 33 647 A1 known.
- a controllable lubricant pump (Vane pump) with automatic pressure control with an in described a housing on one side pivoted cam ring, whose eccentricity from the pumped medium Pressure medium area by means of a spring biased counter bracket control device is adjustable, as well as with suction and pressure openings in the housing, whereby to the radial Support the wing of said vane pump against the Hubring at least two guide rings in chambers on the two End faces of the rotor body are arranged radially movable and a channel connects the pressure side with the chambers.
- the counter bracket biased by a compression spring a stop has and the control device on the to tap the Hubringes opposite side is a control piston, the Inside via a control line directly with the pressure side of the pump connected is.
- the application of the present invention is not limited to vane pumps.
- the invention can also be applied to all controllable pumps, in particular also to those that only have a so-called loss control, i.e. which, when a predeterminable pressure is exceeded, excess lubricant over a Bypass bypass at points of consumption, only the pumped through the system Lubricant quantity (effective delivery quantity) is reduced, but not that by the pump self-funded amount.
- loss control i.e. which, when a predeterminable pressure is exceeded, excess lubricant over a Bypass bypass at points of consumption, only the pumped through the system Lubricant quantity (effective delivery quantity) is reduced, but not that by the pump self-funded amount.
- adjustable Pumps preferred, in which the delivery capacity of the pumps or their Delivery volume and not only the effective delivery volume can be influenced.
- the term "effective delivery volume” is the volume of the lubricant understood which per unit of time through the consumption points, the corresponding feed and Discharges and any upstream units, such as Oil filter, under pressure is pumped. Oil which e.g. via bypass lines and to a pump sump is not considered part of the effective funding volume. That too Drainage of oil via bypass lines limits the pressure at the pump outlet and in entire system, whereby however no energy saving can be achieved. A noteworthy Energy reduction is only achieved if the pump-driven pump is used from the outset Volume is adapted to the requirements as with variable vane pumps or with multi-stage Constant pumps with register control.
- Lubricant pumps of this type are primarily used for supplying lubrication points on internal combustion engines, in particular for motor vehicles.
- the lubricant requirement or minimum requirement of an internal combustion engine is, however, of a number different factors.
- the operating temperature is a key factor here the engine and / or the relevant lubrication points as well as the lubricant.
- the oil generally used as a lubricant When cold, the oil generally used as a lubricant has a high viscosity and is difficult to push through narrow gaps in the lubrication points. At the same time, however, the lubricant requirement is also in the cold state of the internal combustion engine not excessively high, since the parts that move against each other in the cold state in general also have a smaller game against each other and the viscosity of the oil is large and therefore less oil can be passed through.
- a pressure limitation is usually provided, which is either too much derives pumped lubricant via a bypass or the pump delivery rate immediately limited, so that the delivered lubricant at the predetermined limit pressure can be conveyed through the lubricant system.
- the flow resistance in the lubricant system decreases, so that the delivery rate gradually can be increased, which happens, among other things, that the pressure is slightly below of the limit pressure drops, as a result of which the effective delivery rate or the pump output is increased accordingly.
- the control characteristic of the known controllable pumps is included generally set so that the outlet pressure remains approximately constant and only the delivery rate varies depending on the flow resistance in the lubricant system.
- the design point for the pump capacity is the oil requirement of the engine at idling speed when hot and with a correspondingly low-viscosity oil. Even in this condition Provide the pump with a certain minimum flow rate and thus a certain minimum oil pressure, the pump shaft generally being directly coupled to the motor, as previously mentioned.
- the volumetric efficiency of the oil pumps decreases with decreasing temperature due to lower leakage losses.
- the oil consumption of the Motors with falling temperature.
- the engine throughputs of the Figure 1 does not reflect the amount of oil the engine actually has at the specified Speed and temperature as a minimum amount of lubricant, but only what he needs at constant pressure and the specified temperatures and speeds of lubricant records. The conveyance of lubricant that is not actually required in this quantity under pressure naturally costs energy.
- this object is achieved in that a temperature and / or a speed detection an additional one from any pressure-dependent regulation independent regulation or limitation of the effective delivery volume takes place.
- the temperature control permitted flow rate increases with temperature.
- control device which has a temperature sensor and / or a speed sensor and an actuator which regardless of any pressure control, the effective delivery rate depending on the Temperature and / or speed reduced.
- independent of any pressure control means in the sense of the present Invention does not necessarily mean that the temperature or speed control without any influence to the pressure control or from any pressure control in any operating condition remains unaffected, but only that temperature and / or speed as an additional, independent parameters for the setting of an oil flow and the resulting Oil pressure can be used.
- the delivery rate is not only set so that at the points of consumption or any upstream or downstream aggregates, a specifiable maximum pressure is not exceeded, Instead, depending on the temperature and / or the speed, an additional further limitation of the flow rate can be adjusted so that the pressure at the outlet of the Pump or at the pressure measuring points provided for pump control still clearly remains below the predefinable maximum pressure, namely when the system z. B. at the suitable points measured temperature or in the low speed range has correspondingly lower lubricant requirements, so that the lubricant is not below the in particularly critical operating conditions require higher pressure or in a corresponding smaller amount must be provided (see Figure 2).
- the lubricant pump according to the invention is an adjustable vane pump.
- Adjustable vane pumps have the advantage that the mechanical adjustment of their cam ring in a relatively simple way Delivery volume can be adjusted. This has the advantage that the pump shaft directly with the Motor can be coupled and still a regulation of the delivery volume independent of the motor is possible.
- other control devices are also conceivable, with which For example, the speed at which a lubricant pump is driven via pressure and / or temperature-related actuators is regulated. However, this requires one independent drive for the pump.
- a wedge with a Thermostats such as a bimetallic strip, are provided, the one of which has a wedge flank the cam ring engages so that the cam ring is adjusted when the wedge is displaced.
- a bimetal strip for example, can be part of the actuator or as an actuator itself are provided, such a bimetallic strip also being designed and can be arranged that, if desired, it engages directly with the cam ring and this is adjusted depending on the temperature of the bimetal strip.
- Measurement and control can also take place, for example, via electrical elements, such as temperature-dependent electrical components, especially resistors, in an electrical Control loop are measured and emit an electrical signal as an output variable, the one adjustment of an actuator corresponding to the electrical signal.
- electrical elements such as temperature-dependent electrical components, especially resistors
- a special case of such a system is e.g. a stepped piston, one part of the surface for Pressure control from the outlet pressure of the pump or the pressure at a point of consumption is applied.
- Another surface of the stepped piston can optionally be pressurized depending on the speed or temperature via a temperature or speed-controlled valve.
- a temperature or speed-controlled valve At low temperature or speed, for example Valve must be open so that pressure is also applied to the second partial surface of the stepped piston is, which leads to a stronger adjustment of the stepped piston, so that the cam ring is set that there is a smaller delivery volume and thus a relatively small operating pressure sets.
- the valve is switched over the temperature or Speed control closed, so that only a smaller area of the piston of Pressure is applied so that the pump to a higher outlet pressure and a higher Delivery rate is set.
- the corresponding control and activation elements should be as simple as possible, so that the pump as a whole does not become much more complicated. This is especially true for the Use of the pump in standard situations, e.g. in internal combustion engines. In case of Motors or generally systems with a need for lubricants that change very strongly Operating conditions are exposed, but can also be a more complex temperature control the amount of lubricant appropriate and reasonable, provided that this additional effort correspondingly large energy savings due to the possible reduction in the amount of lubricant delivered.
- the pressure in the feed lines to the engine has always the same value (e.g. 5 bar).
- This pressure is designed so that in the most critical state, i.e. with the greatest oil demand, So at the highest temperature and the highest speed, with an oil of the lowest permissible viscosity the oil requirement of the engine is still covered.
- a vane pump 1 with an adjustable lifting ring 2 is shown schematically in FIG.
- a temperature controller for the eccentricity of the cam ring 2 is also shown schematically with respect to the pump shaft 6.
- the temperature controller 3 consists of a temperature sensor or a thermosensitive element 4, a wedge 5 and a spring 7, which are in a row next to the Cam ring are arranged.
- the temperature controller 3 is located inside, for example Pump housing and is in direct contact with the oil to be pumped, which by radial Openings penetrate into the cam ring and through axial openings in the pump housing again can leak. So that the thermosensitive element 4 is essentially at the temperature of the lubricant held.
- element 4 could be, for example Be an element whose thermal expansion is relative in the temperature range of interest is large (for example, element 4 could contain a gas volume).
- element 4 could contain a gas volume.
- a compression spring 9 is provided, for example, which on a Actuating pin 10 of the cam ring 2 acts and this up against a flank of the wedge presses.
- the cam ring 2 is relative to the pump shaft 6 so arranged that the cam ring eccentricity with respect to the shaft 6 by pivoting the Hubringes 2 upward about the axis 8, so when the wedge 5 moves to the right.
- the cam ring 2 is flanked by one edge of the wedge 5 pressed down against the action of the spring 9 when the temperature of the lubricant system decreases or is lower, the wedge 5 shifting from right to left.
- Suitable guides can ensure that the wedge 5 is not in the transverse direction to his can shift the intended travel range.
- the vane pump can be essentially identical to the vane pump 4, only the control direction 3 is by a leaf spring or a bimetallic strip 4 ' replaced, which simultaneously the function of a temperature sensor and an actuator takes over. As the temperature increases, the two are firmly connected Metal strips of the bimetallic strip 4 'differ, so that depending on the relative arrangement of these two metal elements, the curvature of the leaf spring 4 'increases or decreases and the Eccentricity of the cam ring 2 with respect to the pump shaft is reduced accordingly or is enlarged.
- an electrically controllable temperature controller is shown as an actuator 5, the measured by a temperature sensor and measured in a corresponding Control signal is implemented, which adjusts the cam ring in the desired direction, i.e. so, that its eccentricity increases with the temperature of the lubricant.
- the remaining Details of the preload of the cam ring 2 by a spring 9 and the relative arrangement of lifting ring 2, bearing axis 8 and pump shaft 6 can with the embodiment of Figure 4 in be essentially identical.
- FIG. 7 shows a further variant of the adjustment of the lifting ring of a vane pump shown.
- a first partial area 11 of the step piston 5 constantly acted upon by the outlet pressure P2 of the pump, so that this provides a maximum pressure limitation.
- a second stage of the Piston 5 on a surface 12 to which a pressure P1 can be applied which is the simplest Case is identical to pressure P2 and comes from the same source.
- a controllable valve 13 is provided, which switches depending on the temperature and / or speed.
- the valve 13 can be opened be so that both surfaces 11 and 12 are pressurized and thereby a larger Total force against the spring 9 acts as if only the surface 11 were pressurized.
- the cam ring and shaft of the vane pump are arranged so that the eccentricity of the Lift ring by moving the actuator or step piston 5 down in Figure 7 is reduced.
- the valve 13 With increasing temperature and / or speed, the valve 13 is closed, see above that only the surface 11 is pressurized and the cam ring under the effect of Spring 9 again in the direction of greater eccentricity and thus a higher delivery rate Vane pump is adjusted.
- the valve can not only be temperature-dependent, but can also be switched depending on the speed. You have in addition to the pure Maximum pressure limitation and delivery volume control an additional limitation of the Delivery volume depending on the temperature and / or the speed of the motor.
- the structure of the pump is somewhat reduced by the additional control elements provided more complicated, but the energy savings that can be achieved with the pump outweigh these small ones Disadvantage without further ado, especially since the embodiment according to FIG. 5 is a very simple implementation of the additional control according to the invention shows.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Details And Applications Of Rotary Liquid Pumps (AREA)
- Lubrication Of Internal Combustion Engines (AREA)
- Rotary Pumps (AREA)
- Control Of Positive-Displacement Pumps (AREA)
Claims (2)
- Procédé pour régler la puissance de pompage d'une pompe à lubrifiant, dans laquelle au-dessus de la pression qui règne à la sortie de la pompe ou à l'emplacement d'un appareil d'utilisation, la puissance de pompage effective est réduite au moyen d'une régulation qui dépend de la pression,
caractérisé en ce
qu'une limitation indépendante supplémentaire de la puissance de refoulement est exécutée au moyen d'une détection de la température et/ou de la vitesse de rotation, la quantité de refoulement autorisée au moyen de la régulation de température étant limitée par rapport à la quantité de refoulement autorisée par la régulation qui dépend de la pression, lorsque la température et/ou la vitesse de rotation augmentent. - Pompe à lubrifiant réglable, notamment pompe cellulaire à palettes, comportant un dispositif de régulation (2) commandé par la pression,
caractérisée en ce
qu'il est prévu un dispositif de régulation (3) comportant un capteur de la vitesse de rotation et/ou un capteur de température (4) et un organe de réglage (5) qui, en dehors du dispositif de régulation de la pression, règlent la quantité de refoulement effective en fonction de la vitesse de rotation et/ou de la température, l'élément de régulation de la pompe à lubrifiant pouvant être commandé électriquement, et l'organe de réglage (5) étant un piston étagé, dont au moins une partie peut être chargée par une pression par l'intermédiaire d'une soupape (13) pouvant être commandée en fonctionn de la température.
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE4302610A DE4302610C2 (de) | 1993-01-30 | 1993-01-30 | Verfahren zum Regeln der Pumpleistung von Schmiermittelpumpen und Schmiermittelpumpe hierfür |
DE4302610 | 1993-01-30 | ||
PCT/DE1994/000087 WO1994017308A1 (fr) | 1993-01-30 | 1994-01-27 | Procede de regulation de la capacite de pompage de pompes a lubrifiant et pompe a lubrifiant appropriee |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0681656A1 EP0681656A1 (fr) | 1995-11-15 |
EP0681656B1 true EP0681656B1 (fr) | 1998-04-08 |
Family
ID=6479271
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP94905653A Expired - Lifetime EP0681656B1 (fr) | 1993-01-30 | 1994-01-27 | Procede de regulation de la capacite de pompage de pompes a lubrifiant et pompe a lubrifiant appropriee |
Country Status (9)
Country | Link |
---|---|
US (1) | US5800131A (fr) |
EP (1) | EP0681656B1 (fr) |
JP (1) | JPH08505919A (fr) |
KR (1) | KR960700414A (fr) |
CN (1) | CN1051358C (fr) |
BR (1) | BR9406194A (fr) |
DE (1) | DE4302610C2 (fr) |
ES (1) | ES2117251T3 (fr) |
WO (1) | WO1994017308A1 (fr) |
Families Citing this family (60)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE4444819A1 (de) * | 1994-12-15 | 1996-06-20 | Bayerische Motoren Werke Ag | Schmierölpumpe einer Brennkraftmaschine |
DE19513767B4 (de) * | 1995-04-13 | 2004-07-22 | Moog Gmbh | Verstellbare, hydrostatische Radialkolbenmaschine |
DE19513987C2 (de) * | 1995-04-13 | 1998-10-08 | Bosch Gmbh Robert | Verstellbare, hydrostatische Radialkolbenmaschine |
DE19533686C2 (de) * | 1995-09-12 | 1997-06-19 | Daimler Benz Ag | Regelbare Flügelzellenpumpe als Schmiermittelpumpe |
CN1047824C (zh) * | 1996-05-23 | 1999-12-29 | 张金玉 | 间歇式油泵 |
DE19915738A1 (de) * | 1999-04-08 | 2000-10-12 | Bayerische Motoren Werke Ag | Mengenregelbare Flügelzellenpumpe |
DE19915739A1 (de) * | 1999-04-08 | 2000-10-12 | Bayerische Motoren Werke Ag | Mengenregelbare Flügelzellenpumpe |
DE19962554C2 (de) * | 1999-12-23 | 2002-05-16 | Daimler Chrysler Ag | Regelbare Pumpe |
US6623250B2 (en) | 2000-02-17 | 2003-09-23 | Goodrich Pump And Engine Control Systems, Inc. | Fuel metering unit |
US6790013B2 (en) | 2000-12-12 | 2004-09-14 | Borgwarner Inc. | Variable displacement vane pump with variable target regulator |
DE10161131B4 (de) | 2000-12-12 | 2013-11-07 | Slw Automotive Inc. | Flügelpumpe veränderlicher Verdrängung |
US7674095B2 (en) | 2000-12-12 | 2010-03-09 | Borgwarner Inc. | Variable displacement vane pump with variable target regulator |
DE10102531A1 (de) * | 2001-01-20 | 2002-07-25 | Guenther Beez | Stelleinrichtung für eine mengenregelbare Zellenpumpe |
DE10124564A1 (de) * | 2001-05-14 | 2002-11-28 | Joma Hydromechanic Gmbh | Verfahren zum Verstellen einer volumenstromvariablen Verdrängerpumpe in einem Brennkraftmotor |
DE10223466B4 (de) * | 2001-05-31 | 2015-07-02 | Magna Powertrain Hückeswagen GmbH | Pumpe |
EP1350930B2 (fr) * | 2002-04-03 | 2016-01-27 | SLW Automotive Inc. | Pompe à déplacement variable et dispositif de contrôle |
US7726948B2 (en) | 2002-04-03 | 2010-06-01 | Slw Automotive Inc. | Hydraulic pump with variable flow and variable pressure and electric control |
DE10239364A1 (de) * | 2002-08-28 | 2004-03-18 | Dr.Ing.H.C. F. Porsche Ag | Einrichtung zur Regelung der Pumpleistung einer Schmiermittelpumpe für eine Brennkraftmaschine |
US6962485B2 (en) * | 2003-04-14 | 2005-11-08 | Goodrich Pump And Engine Control Systems, Inc. | Constant bypass flow controller for a variable displacement pump |
US6996969B2 (en) * | 2003-09-09 | 2006-02-14 | Goodrich Pump & Engine Control Systems, Inc. | Multi-mode shutdown system for a fuel metering unit |
BR0304633B1 (pt) * | 2003-10-21 | 2012-03-20 | motor de combustão interna, cabeçote de motor e tubulação para distribuição de combustìvel | |
US20050100447A1 (en) * | 2003-11-11 | 2005-05-12 | Desai Mihir C. | Flow control system for a gas turbine engine |
ITBO20040008A1 (it) * | 2004-01-09 | 2004-04-09 | Pierburg Spa | Impianto di pompaggio |
US7322800B2 (en) * | 2004-04-16 | 2008-01-29 | Borgwarner Inc. | System and method of providing hydraulic pressure for mechanical work from an engine lubricating system |
US9181803B2 (en) | 2004-12-22 | 2015-11-10 | Magna Powertrain Inc. | Vane pump with multiple control chambers |
EP3165769B1 (fr) | 2004-12-22 | 2018-12-12 | Magna Powertrain Inc. | Procédé de fonctionnement d'une pompe à capacité variable |
CN100399009C (zh) * | 2005-03-24 | 2008-07-02 | 上海交通大学 | 汽车机油泵通用特性的自动测试方法 |
DE102005041388A1 (de) * | 2005-09-01 | 2007-03-08 | Zf Lenksysteme Gmbh | Rotationspumpe |
DE102005048602B4 (de) * | 2005-10-06 | 2011-01-13 | Joma-Polytec Kunststofftechnik Gmbh | Flügelzellenmaschine, insbesondere Flügelzellenpumpe |
KR101131290B1 (ko) * | 2005-10-06 | 2012-03-30 | 조마 폴리텍 쿤스츠토프테닉 게엠바하 | 베인셀펌프 |
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 |
KR101259220B1 (ko) * | 2006-07-06 | 2013-04-29 | 마그나 파워트레인 인크. | 이중 스프링을 구비한 가변 용량 펌프 |
DE102006037461A1 (de) * | 2006-08-10 | 2008-02-14 | Bayerische Motoren Werke Ag | Verfahren der Betätigung einer volumenstromregelbaren Schmiermittelpumpe im Schmiermittelkreislauf eines Dieselmotors |
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 |
DE102006049620A1 (de) * | 2006-10-20 | 2008-04-24 | Bayerische Motoren Werke Ag | Druckregelvorrichtung |
DE102006059965A1 (de) * | 2006-12-19 | 2008-06-26 | GM Global Technology Operations, Inc., Detroit | Pumpe mit steuerbarem Durchsatz und Anwendungen dafür |
DE102006061326B4 (de) | 2006-12-22 | 2012-02-16 | Mahle International Gmbh | Stelleneinrichtung für eine mengenregelbare Zellenpumpe |
DE102007002677A1 (de) | 2007-01-18 | 2008-07-24 | Bayerische Motoren Werke Aktiengesellschaft | Verfahren der Betätigung einer volumenstromregelbaren Schmiermittelpumpe im Schmiermittelkreislauf eines Dieselmotors |
KR20110014691A (ko) * | 2008-05-30 | 2011-02-11 | 메탈딘 엘엘씨 | 가변 출력 유체 펌프 시스템 |
DE112009003823B4 (de) | 2008-12-23 | 2022-11-10 | Hanon Systems Efp Deutschland Gmbh | Pumpenanordnung |
IT1392918B1 (it) * | 2009-02-10 | 2012-04-02 | O M P Officine Mazzocco Pagnoni S R L | Pompa rotativa a palette a cilindrata variabile per un motore per autoveicoli |
KR20120006977A (ko) * | 2009-03-05 | 2012-01-19 | 에스티티 테크놀로지스 인크., 어 조인트 벤쳐 오브 마그나 파워트레인 인크. 앤드 에스하베 게엠베하 | 직접 제어 선형 가변 베인펌프 |
EP2264318B1 (fr) * | 2009-06-16 | 2016-08-10 | Pierburg Pump Technology GmbH | Pompe lubrifiante à déplacement variable |
DE102009039776A1 (de) * | 2009-09-02 | 2011-03-03 | Audi Ag | Vorrichtung und Verfahren zur Regelung eines Schmierölstroms, insbesondere zur Kühlung und Schmierung eines Getriebes |
CN101846237B (zh) * | 2010-03-03 | 2012-11-21 | 南京腾源机械制造有限公司 | 机油泵专用泵轴及机油泵 |
DE102010019007A1 (de) * | 2010-05-03 | 2011-11-03 | Gm Global Technology Operations Llc (N.D.Ges.D. Staates Delaware) | Schmierstoffkreislauf |
DE102010022677B4 (de) | 2010-06-04 | 2016-06-30 | Nidec Gpm Gmbh | Flügelzellenpumpe |
GB2486195A (en) * | 2010-12-06 | 2012-06-13 | Gm Global Tech Operations Inc | Method of Operating an I.C. Engine Variable Displacement Oil Pump by Measurement of Metal Temperature |
JP2013193511A (ja) * | 2012-03-16 | 2013-09-30 | Toyota Motor Corp | 車両制御システム |
US9109597B2 (en) | 2013-01-15 | 2015-08-18 | Stackpole International Engineered Products Ltd | Variable displacement pump with multiple pressure chambers where a circumferential extent of a first portion of a first chamber is greater than a second portion |
CN105264230B (zh) * | 2013-05-24 | 2017-01-18 | 皮尔伯格泵技术有限责任公司 | 可变排量润滑油泵 |
JP6177610B2 (ja) * | 2013-07-17 | 2017-08-09 | 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 |
WO2015058783A1 (fr) * | 2013-10-21 | 2015-04-30 | Pierburg Pump Technology Gmbh | Pompe à lubrifiant à déplacement variable |
US9874209B2 (en) * | 2014-02-11 | 2018-01-23 | Magna Powertrain Bad Homburg GmbH | Variable displacement transmission pump and controller with adaptive control |
DE102015122649A1 (de) | 2015-12-22 | 2017-06-22 | Schwäbische Hüttenwerke Automotive GmbH | Pumpe mit zwei Stellkolben |
US11242852B2 (en) * | 2019-04-01 | 2022-02-08 | GM Global Technology Operations LLC | Variable displacement oil pump slide with bow spring |
CN110529720A (zh) * | 2019-09-26 | 2019-12-03 | 淄博九洲润滑科技有限公司 | 一种全密封式润滑接力泵 |
CN113494600B (zh) * | 2021-07-26 | 2022-08-23 | 潍柴动力股份有限公司 | 一种异常诊断方法及装置 |
CN114754282B (zh) * | 2022-04-24 | 2024-06-21 | 浙江夏厦精密制造股份有限公司 | 一种改进型汽车用油泵 |
Family Cites Families (12)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2768585A (en) * | 1952-12-18 | 1956-10-30 | Schwitzer Corp | Pump control mechanism |
DE1034482B (de) * | 1957-02-20 | 1958-07-17 | Sueddeutsche Kuehler Behr | Regelbare Drehkolbenpumpe |
US3456593A (en) * | 1967-06-26 | 1969-07-22 | Oscar E Rosaen | Variable capacity mechanism for fluid pumps and motors |
DE2806965A1 (de) * | 1978-02-18 | 1979-08-23 | Integral Hydraulik Co | Verstellbare hydraulische fluegelzellenpumpe |
US4259039A (en) * | 1979-03-20 | 1981-03-31 | Integral Hydraulic & Co. | Adjustable volume vane-type pump |
DE3333647C2 (de) * | 1982-09-21 | 1986-10-30 | Glyco-Antriebstechnik Gmbh, 6200 Wiesbaden | Schmiermittelpumpe für die Druckerzeugung bei einem druckumlaufgeschmierten Verbrennungsmotor |
JPS59136592A (ja) * | 1983-01-24 | 1984-08-06 | Toyoda Mach Works Ltd | 可変容量形ベ−ンポンプ |
JPS59173588A (ja) * | 1983-03-22 | 1984-10-01 | Nippon Radiator Co Ltd | 可変容量型偏心式ロ−タリコンプレツサ |
SE457010B (sv) * | 1983-09-17 | 1988-11-21 | Glyco Antriebstechnik Gmbh | Reglerbar smoerjmedelspump |
JPS6188056A (ja) * | 1984-10-08 | 1986-05-06 | Toyota Motor Corp | 自動変速機のオイルポンプの制御方法 |
DE4011671C2 (de) * | 1990-04-11 | 1994-04-28 | Glyco Metall Werke | Regelbare Flügelzellenpumpe |
USD419481S (en) * | 1999-04-22 | 2000-01-25 | John Duff | Combined golf ball and tee |
-
1993
- 1993-01-30 DE DE4302610A patent/DE4302610C2/de not_active Expired - Lifetime
-
1994
- 1994-01-27 EP EP94905653A patent/EP0681656B1/fr not_active Expired - Lifetime
- 1994-01-27 BR BR9406194A patent/BR9406194A/pt not_active Application Discontinuation
- 1994-01-27 ES ES94905653T patent/ES2117251T3/es not_active Expired - Lifetime
- 1994-01-27 KR KR1019950703086A patent/KR960700414A/ko not_active Application Discontinuation
- 1994-01-27 JP JP6516573A patent/JPH08505919A/ja active Pending
- 1994-01-27 US US08/500,937 patent/US5800131A/en not_active Expired - Fee Related
- 1994-01-27 WO PCT/DE1994/000087 patent/WO1994017308A1/fr active IP Right Grant
- 1994-01-27 CN CN94191057A patent/CN1051358C/zh not_active Expired - Fee Related
Also Published As
Publication number | Publication date |
---|---|
DE4302610C2 (de) | 1996-08-08 |
ES2117251T3 (es) | 1998-08-01 |
CN1117307A (zh) | 1996-02-21 |
JPH08505919A (ja) | 1996-06-25 |
US5800131A (en) | 1998-09-01 |
CN1051358C (zh) | 2000-04-12 |
BR9406194A (pt) | 1995-12-12 |
DE4302610A1 (de) | 1994-08-04 |
WO1994017308A1 (fr) | 1994-08-04 |
KR960700414A (ko) | 1996-01-20 |
EP0681656A1 (fr) | 1995-11-15 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
EP0681656B1 (fr) | Procede de regulation de la capacite de pompage de pompes a lubrifiant et pompe a lubrifiant appropriee | |
DE4319200C1 (de) | Mehrstufenregler für Schmiermittelpumpen mit kontinuierlich veränderbarem Fördervolumen | |
DE102004003335B4 (de) | Motorölsystem mit Verstellpumpe | |
DE10237801C5 (de) | Vorrichtung zur Druckregelung von Hydraulikpumpen | |
DE112007001131B4 (de) | Kontinuierlich verstellbare Drehschieberpumpe und entsprechendes System | |
EP2014919B2 (fr) | Soupape de réglage pour le réglage du volume d'alimentation d'une pompe volumétrique | |
DE3333647C2 (de) | Schmiermittelpumpe für die Druckerzeugung bei einem druckumlaufgeschmierten Verbrennungsmotor | |
EP0254077A2 (fr) | Pompe à engrenages internes | |
DE102017006755A1 (de) | Motorölzuführvorrichtung, Verfahren zum Schützen eines Ölfilters und Computerprogrammprodukt | |
DE112015000171T5 (de) | Motorölzufuhrvorrichtung | |
DE102010019007A1 (de) | Schmierstoffkreislauf | |
EP0724068A1 (fr) | Système d'amenée d'huile | |
DE4224973C2 (de) | Fluidversorgungssystem mit Druckbegrenzung | |
DE102015211846A1 (de) | Ablassvorrichtung für Öl-Kreislauf von Motor | |
EP1463888B1 (fr) | Dispositif pour reguler la pression de pompes hydrauliques | |
EP1076164B1 (fr) | Dispositif et procédé de régulation de la pression d'huile dans un moteur à combustion | |
DE3433423A1 (de) | Drehzahlregler fuer kraftstoffeinspritzpumpen | |
DE2753098C2 (de) | Lenkanlage mit hydraulischer Hilfskraftunterstützung | |
DE1905669C3 (de) | Druckregeleinrichtung für das Betriebsdrucköl einer automatischen Kraftfahrzeuggetriebeeinheit | |
DE2539007A1 (de) | Mit vorverdichtung arbeitender verbrennungsmotor | |
DE102009060189A1 (de) | Regelvorrichtung für die Verstellung des Fördervolumens einer Pumpe | |
EP0620368B1 (fr) | Pompe à engrenages | |
DE1908922B2 (de) | Hydraulische Vorrichtung zur stufenlosen Regelung der Drehzahl von Lüftermotoren und zur Verstellung von Hauptkühlerund Nebenkühler Jalousien bei Brennkraftmaschinen, insbesondere in Schienenfahrzeugen | |
DE102006037461A1 (de) | Verfahren der Betätigung einer volumenstromregelbaren Schmiermittelpumpe im Schmiermittelkreislauf eines Dieselmotors | |
EP0315878A2 (fr) | Pompe à engrènement interne |
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: 19950731 |
|
AK | Designated contracting states |
Kind code of ref document: A1 Designated state(s): AT BE CH DE LI |
|
17Q | First examination report despatched |
Effective date: 19960105 |
|
D17P | Request for examination filed (deleted) | ||
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 |
|
GRAH | Despatch of communication of intention to grant a patent |
Free format text: ORIGINAL CODE: EPIDOS IGRA |
|
RAP1 | Party data changed (applicant data changed or rights of an application transferred) |
Owner name: DAIMLER-BENZ AKTIENGESELLSCHAFT |
|
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 |
|
ITF | It: translation for a ep patent filed | ||
AK | Designated contracting states |
Kind code of ref document: B1 Designated state(s): ES FR GB IT |
|
GBT | Gb: translation of ep patent filed (gb section 77(6)(a)/1977) |
Effective date: 19980420 |
|
ET | Fr: translation filed | ||
REG | Reference to a national code |
Ref country code: ES Ref legal event code: FG2A Ref document number: 2117251 Country of ref document: ES Kind code of ref document: T3 |
|
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 | ||
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: GB Payment date: 20000112 Year of fee payment: 7 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: ES Payment date: 20000120 Year of fee payment: 7 |
|
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: 20010127 |
|
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 NON-PAYMENT OF DUE FEES Effective date: 20010129 |
|
GBPC | Gb: european patent ceased through non-payment of renewal fee |
Effective date: 20010127 |
|
REG | Reference to a national code |
Ref country code: ES Ref legal event code: FD2A Effective date: 20020916 |
|
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;WARNING: LAPSES OF ITALIAN PATENTS WITH EFFECTIVE DATE BEFORE 2007 MAY HAVE OCCURRED AT ANY TIME BEFORE 2007. THE CORRECT EFFECTIVE DATE MAY BE DIFFERENT FROM THE ONE RECORDED. Effective date: 20050127 |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: TP |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: CD Ref country code: FR Ref legal event code: CA |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: FR Payment date: 20130219 Year of fee payment: 20 |