EP3676498A1 - Pompe à liquide de refroidissement pouvant être régulée pour un circuit de refoulement principal et un circuit de refoulement secondaire - Google Patents

Pompe à liquide de refroidissement pouvant être régulée pour un circuit de refoulement principal et un circuit de refoulement secondaire

Info

Publication number
EP3676498A1
EP3676498A1 EP18740810.9A EP18740810A EP3676498A1 EP 3676498 A1 EP3676498 A1 EP 3676498A1 EP 18740810 A EP18740810 A EP 18740810A EP 3676498 A1 EP3676498 A1 EP 3676498A1
Authority
EP
European Patent Office
Prior art keywords
pump
valve
circuit
pressure
hydraulic
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP18740810.9A
Other languages
German (de)
English (en)
Other versions
EP3676498B1 (fr
Inventor
Franz Pawellek
Toni Steiner
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.)
Nidec GPM GmbH
Original Assignee
Nidec GPM 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
Application filed by Nidec GPM GmbH filed Critical Nidec GPM GmbH
Publication of EP3676498A1 publication Critical patent/EP3676498A1/fr
Application granted granted Critical
Publication of EP3676498B1 publication Critical patent/EP3676498B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D15/00—Control, e.g. regulation, of pumps, pumping installations or systems
    • F04D15/0005—Control, e.g. regulation, of pumps, pumping installations or systems by using valves
    • F04D15/0022—Control, e.g. regulation, of pumps, pumping installations or systems by using valves throttling valves or valves varying the pump inlet opening or the outlet opening
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D15/00—Control, e.g. regulation, of pumps, pumping installations or systems
    • F04D15/0027—Varying behaviour or the very pump
    • F04D15/0038—Varying behaviour or the very pump by varying the effective cross-sectional area of flow through the rotor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P7/00—Controlling of coolant flow
    • F01P7/14—Controlling of coolant flow the coolant being liquid
    • F01P2007/146—Controlling of coolant flow the coolant being liquid using valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P5/00—Pumping cooling-air or liquid coolants
    • F01P5/10—Pumping liquid coolant; Arrangements of coolant pumps
    • F01P5/12—Pump-driving arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2250/00—Geometry
    • F05D2250/50—Inlet or outlet
    • F05D2250/52—Outlet
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2270/00—Control
    • F05D2270/50—Control logic embodiments
    • F05D2270/54—Control logic embodiments by electronic means, e.g. electronic tubes, transistors or IC's within an electronic circuit
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2270/00—Control
    • F05D2270/60—Control system actuates means
    • F05D2270/64—Hydraulic actuators

Definitions

  • the present invention relates to a mechanically driven coolant pump with a controllable delivery rate for a main charge cycle from a first outlet and for a secondary delivery cycle from a second outlet of the coolant pump.
  • auxiliary equipment such as exhaust gas recirculation, turbocharger, intercooling or the like as well as so-called split cooling, i. Separate cooling of the engine block and cylinder heads of the incinerator is used.
  • split cooling i. Separate cooling of the engine block and cylinder heads of the incinerator is used.
  • systems are known in the prior art both comprising one or more additional water pumps to allow independent circulation of individual circulations, as well as systems with water valves, allow a needs-based distribution of a demanded by a pump coolant flow to different branches.
  • make-up water pumps and water valves with actuators for valve adjustment in a branched pipe network in turn with a corresponding installation and susceptibility of cabling for a power supply and control signal transmission between decentralized actuators or pump motors, a central control device and a battery.
  • the number and independence of the components, failure of a drive, or failure of a cable can affect other areas of the coolant circulation that are inconsistent with a uniform fail-safe mode to prevent consequential damage.
  • German Patent Application DE 102010 050261 B3 of the same Applicant discloses a coolant pump of the so-called ECF (Electromagnetic Controlled Flow) type with a bypass.
  • ECF Electromagnetic Controlled Flow
  • an effective capacity compared to a capacity corresponding to the engine speed can be throttled set or turned off.
  • the regulation takes place by means of a coolant hydraulically actuated, cylindrical control slide, which covers a flow-effective radial region of the pump impeller.
  • the control spool In a closed state, the control spool covers the pump impeller to a volute, thereby shutting off the pump outlet. In this case, an opening is opened to a bypass in a rear wall of the pump chamber behind the pump impeller, which grants a separate to the pump outlet discharge of coolant from the pump chamber.
  • the opening of the bypass to the pump chamber is closed by a part of the rule slide.
  • the disclosed coolant pump thus provides a function of switching a large flow rate through the pump outlet or a small flow rate through the bypass.
  • intermediate states of a partial flow of the delivery flow occur whose course is not separately controllable in the desired way, but adjusts as a function of a pressure difference of the individual volume flows, which in turn results from a fixed flow geometry of the pump results.
  • Another aspect of the invention is also to provide a constructive connection for a jointly implemented in the delivery cycles Fail Safe mode.
  • the controllable mechanical coolant pump with a first outlet for a main conveyor belt and a second outlet for a secondary in-line circuit has i.a. a derived from the coolant hydraulic control circuit with an input side auxiliary pump, an output side proportional valve and a control slide as a hydraulic actuator for für flußbegende / .ung of Hauptfördcrnik- running on, and is characterized in particular by a control valve as a hydraulic actuator for Flow restriction of the secondary conveyor circuit is connected to the hydraulic control circuit, wherein operations of the Regeschiebers and the control valve are assigned to respective pressure ranges in the hydraulic control circuit.
  • the invention provides for the first time a coolant pump with two hydraulic actuators, in particular for the regulation of two different pump outlets or conveying circuits.
  • the invention provides for the first time before two hydraulic actuators on a hydraulic control circuit, which is derived in particular from the coolant to connect, i. to operate with the same control pressure.
  • control valve can be connected as branched-off hydraulic actuator between the auxiliary pump and the proportional valve to the hydraulic control circuit, and be closed by means of the pressure in the hydraulic control circuit against an elastic bias.
  • control valve can be designed as a seat valve, which is acted upon by a spring in the opening direction.
  • the spring-loaded seat valve ensures a smooth guided adjustment of the valve body with respect to the force of the spring even under load absorption of the delivery pressure.
  • a piston surface for receiving a hydraulic actuating force of the control valve in the hydraulic Regelkrcislauf be smaller than a piston area of the control slide in the hydraulic control circuit.
  • This selection of the different hydraulically effective area sizes of the actuators makes an application-specific preference in the hydraulic actuation.
  • a middle region of the control pressure which lies between the respective pressures for closing the control slide and the control valve, that state is implemented, that the control slide for the main conveyor circuit remains closed and the control valve for the slave overhead loop is openably adjustable.
  • This condition is needed, for example, when the internal combustion engine is to reach an operating temperature quickly, while at auxiliary equipment, such as e.g. There is already a need for cooling at a valve of the exhaust gas recirculation.
  • Piston area of the rule slide an area ratio of about 1: 3 amount.
  • control valve may be disposed in the second outlet on the pump housing.
  • a pressure valve which opens above a predetermined pressure difference between a higher pressure in the H nuptlorderstrom and a lower pressure in the secondary flow.
  • the pressure valve thus acts during the transient pressure difference described a drying of the small secondary conveyor circuit against, as a part of the main conveyor circuit flows into the secondary conveyor circuit.
  • the pressure valve may be formed as a check valve, which is acted upon by a spring in the closing direction.
  • a spring-loaded check valve is the preferred means to provide a pressure valve which gradually opens to a subsequent flow from the main conveyor circuit to the secondary conveyor circuit with increasing pressure difference.
  • the pressure valve downstream of the control slide in the main conveyor circuit and upstream of the control valve in the secondary conveyor circuit open.
  • Fig. 1 is an axial sectional view of the pump in a state in which both the
  • Fig. 2 is an axial sectional view of the pump in a state in which the Hauptforderniklauf is closed and the secondary conveying circuit is open;
  • Fig. 3 is an axial sectional view of the pump in a state in which both the
  • Main delivery circuit and the secondary conveyor circuit are open.
  • Fig. 1 shows a longitudinal section through the pump without complete outer contours of a pump housing 1.
  • a pump shaft 3 extends from a pulley 4, through a shaft bearing in a pump chamber 10 of the pump housing 1 and drives a pump impeller 2 at.
  • the pump impeller 2 and the pump chamber 10, which is not fully shown, are configured in the construction of a radial pump assembly in which a pump inlet 13 (not shown), the pump impeller 2 flows axially, and a first pump outlet 1 1 for connected to the internal combustion engine II
  • the main part of the pump chamber is tangentially out of the pumping chamber 10 via a radially outer spiral casing section.
  • the Pumpenbaugruppc the coolant pump has a hydraulically adjustable control slide 8, which is known from a so-called ECF pump type.
  • a flow-effective radial area around the impeller 2 of the control slide 8 with a coaxial with the pump shaft 3 formed cylindrical portion along a parallel to the pump shaft 3 extending travel are covered variable.
  • the control slide 8 is in a closed position, in which the flow area of the pump impeller 2 is completely covered and thus no flow to the first pump outlet 1 1 is effected.
  • the pump housing 1 is also within the radius of the pump impeller 2 and parallel to the pump shaft 3 a Axialkolbcnpumpe 6 (shown schematically) arranged, the piston via a shoe (not shown) is actuated on a rotatably mounted with the pump shaft 3 swash plate (not shown) slides.
  • the axial piston pump 6 serves as an auxiliary pump of a hydraulic control circuit 5 operated with coolant (shown schematically), in which a flow rate independent of the control flow 8 and a control valve 9 described later is generated and adjusted.
  • the axial piston pump 6 sucks in coolant from the Strömungsbercich between the pump impeller 2 and the rule slide 9 and pushes the pressurized refrigerant in the hydraulic Rege Vietnameselauf 5, which is formed in the pump housing 1.
  • the hydraulic control circuit 5 comprises an electromagnetically actuated proportional valve 7 (shown schematically), which limits a return of the coolant in the pumped coolant flow and thus sets a pressure of the hydraulic Regeniklaufs 5 in a distance between the Axialkolbcnpumpe 6 and the proportional valve 7.
  • a hydraulic branch supplies the pressure of the hydraulic recirculation loop 5 to an annular piston 1 8, which is arranged coaxially with the Pumpenwcllc 3 and assumes the function of a hydraulic actuator along the displacement path of the control slide 8.
  • a return spring acts on the annular piston 18 in the opposite direction to the pressure of the hydraulic control circuit 5, ie away from the pump impeller 2.
  • the annular piston 1 8 communicates with the Regclschieber 8 and moves it with increasing pressure of the hydraulic control circuit 5 in the direction of the pump impeller second , whereby the cylindrical portion of the control slide 6 is increasingly brought into axial overlap with the pump impeller 2.
  • the electromagnetic proportional valve 7 is opened without supplying a drive current, so that the coolant sucked in by the axial piston pump 6 flows back, essentially without pressure, via the hydraulic regulator circuit 5 through the proportional valve 7 back into the required coolant. If the electromagnetic proportional valve 7 is closed by supplying a controlled pulse width modulation drive current in a second or intermittent manner, the pressure generated by the axial piston pump 6 spreads via the hydraulic control circuit 5 to the annular piston 1 8. If the proportional valve 7 remains open by switching off the drive current, no pressure builds up in the hydraulic control circuit 5 and the annular piston 18 returns under the action of the return spring in the unactuated basic position.
  • the pump housing 1 comprises a second pump outlet 12 for a Mau complicat Vietnamese , to which in the present embodiment, a cooling system for an exhaust gas recirculation valve (EGR Vcntil) is connected .
  • the second pump outlet 12 opens at a rear side of the pump impeller 2 in the pump chamber 10. Die Mouth of the second pump outlet 12 is the same accessible through frontal openings of the control slide 8 regardless of a position, so that always a portion of the flow from the pump chamber 10 into the second pump outlet 12 penetrates.
  • the control valve 9 is arranged, which blocks, limits or opens a flow of the secondary conveyor circuit.
  • the control valve 9 is also connected by a hydraulic branch with the hydraulic control circuit 5.
  • a valve body of the Regelvcntils 9 is displaced by the pressure in the hydraulic control circuit 5 approximately perpendicular to the flow direction against the restoring force of a spring and thereby gradually closes the flow in the second pump outlet 12. At lower hydraulic control pressure, the valve body of the control valve 9 is pushed back by the spring and the flow of the second pump outlet 12 is released.
  • the pressure in the hydraulic control circuit 5 is controlled by on and off periods for opening and closing the Proporti onal valve s 7.
  • To control the control valve 9 in a variable position for limiting the flow of pressure is controlled so that a balance between the hydraulic pressure and a restoring force of the prestressed spring in the control valve 9 is achieved and a position of the valve body is held in the control valve 9.
  • the positions of the valve body of the control valve 9 as well as a position of the annular piston 18 of the control valve 8 by a displacement sensor (not shown) detected and used to control the proportional valve 7 s.
  • throttling of the main delivery cycle and the sub-delivery cycle with respect to a predetermined engine speed is performed on the basis of a control current for opening and closing the solenoid-operated proportional valve 7.
  • the hydraulic design has been selected such that the control valve 9 for the secondary conveyor circuit a higher hydraulic see pressure to close needed as the slide valve 8 for the main conveyor circuit.
  • the assignment of the pressure ranges in which the hydraulic actuators respond is set by means of a hydraulically effective piston surface, which has each actuator for pressure absorption from the hydraulic control circuit 5, and the selected characteristic of the return springs.
  • the response of the two hydraulic actuators is preferably selected such that an adjustment of the control valve 9 can be controlled by a pressure which starts above a pressure at which the control slide 8 completely closes.
  • a suitable separation between the pressure to close the one hydraulic actuator and the lower pressure at the beginning of the adjustment of the other actuator is set by a hydraulically effective area ratio.
  • the area ratio between the higher pressure closing actuator and the lower pressure closing actuator is 1: 3.
  • the operating state of the controllable coolant pump shown in FIG. 1 is intended for a cold start situation of a vehicle, in which there is still no cooling requirement of the internal combustion engine or of other devices.
  • the proportional valve 7 is controlled by a control unit (not shown) by a sampling ratio of a Pul swei t enmod u 1 ati on with a high proportion of switch-on to set a high pressure in the hydraulic control circuit 5.
  • the proportional valve 7 limits a return flow of the coolant behind the axial piston pump 6 and a backwater in front of the proportional proportional valve 7 causes the pressure in the hydraulic control circuit 5 to increase the branched actuators until the Regclschieber 8 and subsequently close the control valve 9. From a hold of a pressure at which the control valve 9 completely closes, both flows of the main conveyor and the NcbenANCwanspilaufs are therefore limited or closed maximum.
  • the operating state of the controllable coolant pump shown in FIG. 2 is intended, for example, for a warm-up situation of a vehicle in which the internal combustion engine is not yet at operating temperature, but have already formed so-called hotspots at facilities such as an exhaust gas recirculation, so that already a cooling requirement for the protection of Components such as an EGR valve is present.
  • the proportional valve 7 is controlled by a sampling ratio of a pulse width modulation with a lower proportion of switch-on to lower the pressure in the hydraulic control circuit 5.
  • a return flow from the hydraulic control circuit 5 through the proportional valve 7 increases and the pressure on the actuators decreases.
  • a gradual limitation of the secondary conveying circuit with the main request circuit closed is adjustable.
  • the pressure valve 15 in turn remains closed, since it continues to be exposed in the closing direction to a pressure of the secondary conveying circuit while the other side is not exposed to a delivery pressure.
  • the operating state of the controllable cooling medium pump shown in FIG. 3 is intended for a load situation of a vehicle in which there is a need for cooling both for the combustion engine and for one or more other devices which are connected to the auxiliary conveying circuit.
  • the proportional valve 7 is not or driven by a sampling ratio of a pulse width modulation with a small proportion of switch-on, so no pressure is generated in the hydraulic control circuit 5.
  • the control slide 8 moves over gradual limiting positions in the open position, while the already open control valve 9 remains open.
  • both the flow of the main conveyor slices and the flow rate of the auxiliary conveyor circuit 5 remain open to the maximum.
  • a gradual limitation of the main conveyor circuit with an open secondary conveyor circuit is adjustable.
  • the pressure valve 15 is opened during the opening of the control slide 8 or during a maximum open main conveying circuit by a pressure difference.
  • the pressure difference results from a slight pressure loss of the part of the delivery flow flowing into the main conveyor and a high pressure loss of the part of the delivery flow which flows into the secondary delivery circuit.
  • a corresponding pressure drop in the second pump outlet 12 increases the pressure difference at the pressure valve 15.
  • the pressure valve 15 opens and allows a subsequent flow from the large flow rate in the main conveyor circuit to compensate for the insufficient flow rate in the secondary conveyor cycle.
  • the flow behavior during a transient state of division or a relatively large division ratio between the delivery quantities is improved.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Control Of Positive-Displacement Pumps (AREA)

Abstract

L'invention concerne une pompe à liquide de refroidissement à entraînement mécanique présentant une capacité de refoulement pouvant être régulée pour un circuit de refoulement principal provenant d'une première sortie et pour un circuit de refoulement secondaire provenant d'une deuxième sortie de la pompe à liquide de refroidissement. La pompe présente entre autres un circuit de régulation hydraulique (5) dévié du liquide de refroidissement pourvu d'une pompe auxiliaire (6) côté entrée, d'une soupape proportionnelle (7) côté sortie et d'un tiroir de régulation (8) faisant office d'actionneur hydraulique destiné à limiter le débit du circuit de refoulement principal, une partie cylindrique du tiroir de régulation (8) pouvant coulisser axialement dans la chambre de pompe (10) aux fins de protection radiale de la roue à aubes (2) de la pompe, et ce au moyen d'une pression dans le circuit de régulation hydraulique (5) à l'encontre d'une force de rappel. La pompe à liquide de refroidissement se caractérise en particulier par le fait qu'une soupape (9) de régulation faisant office d'actionneur hydraulique destiné à limiter le débit du circuit de refoulement secondaire est reliée au circuit de régulation hydraulique (5), des actionnements du tiroir de régulation (8) et de la soupape (9) de régulation étant associés à des zones de pression respectives dans le circuit de régulation hydraulique (5).
EP18740810.9A 2017-09-01 2018-07-12 Pompe à liquide de refroidissement pouvant être régulée pour un circuit de refoulement principal et un circuit de refoulement secondaire Active EP3676498B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102017120191.2A DE102017120191B3 (de) 2017-09-01 2017-09-01 Regelbare Kühlmittelpumpe für Haupt- und Nebenförderkreislauf
PCT/EP2018/068958 WO2019042644A1 (fr) 2017-09-01 2018-07-12 Pompe à liquide de refroidissement pouvant être régulée pour un circuit de refoulement principal et un circuit de refoulement secondaire

Publications (2)

Publication Number Publication Date
EP3676498A1 true EP3676498A1 (fr) 2020-07-08
EP3676498B1 EP3676498B1 (fr) 2021-06-09

Family

ID=62916672

Family Applications (1)

Application Number Title Priority Date Filing Date
EP18740810.9A Active EP3676498B1 (fr) 2017-09-01 2018-07-12 Pompe à liquide de refroidissement pouvant être régulée pour un circuit de refoulement principal et un circuit de refoulement secondaire

Country Status (6)

Country Link
US (1) US11002281B2 (fr)
EP (1) EP3676498B1 (fr)
CN (1) CN111051702B (fr)
BR (1) BR112019028100A2 (fr)
DE (1) DE102017120191B3 (fr)
WO (1) WO2019042644A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP4341538B1 (fr) * 2021-05-20 2025-04-30 Pierburg Pump Technology GmbH Pompe mécanique à liquide de refroidissement pour véhicule à moteur pouvant être commandée

Family Cites Families (33)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10047387B4 (de) 2000-09-25 2013-09-12 GPM Geräte- und Pumpenbau GmbH Dr. Eugen Schmidt, Merbelsrod Elektrisch angetriebene Kühlmittelpumpe
DE10207653C1 (de) 2002-02-22 2003-09-25 Gpm Geraete Und Pumpenbau Gmbh Elektrische Kühlmittelpumpe mit integriertem Ventil, sowie Verfahren zu dessen Steuerung
DE10314526B4 (de) 2003-03-31 2007-11-29 Geräte- und Pumpenbau GmbH Dr. Eugen Schmidt Kühlmittelpumpe, insbesondere strömungsgekühlte elekrische Kühlmittelpumpe mit integriertem Wegeventil
DE102004012383B3 (de) 2004-03-13 2005-06-02 Faurecia Autositze Gmbh & Co. Kg Steuerungsmodul für eine Fahrzeugsitz-Verstelleinrichtung
DE102005062200B3 (de) 2005-12-23 2007-02-22 Geräte- und Pumpenbau GmbH Dr. Eugen Schmidt Regelbare Kühlmittelpumpe
JP2007231907A (ja) 2006-03-03 2007-09-13 Denso Corp 燃料供給装置
DE102006048255A1 (de) 2006-10-12 2008-04-17 Zf Friedrichshafen Ag Vorrichtung zur elektronischen Steuerung eines Automatgetriebes für ein Kraftfahrzeug
DE102007042866A1 (de) 2007-09-08 2009-03-12 Geräte- und Pumpenbau GmbH Dr. Eugen Schmidt Regelbare Kühlmittelpumpe
DE102008022354B4 (de) 2008-05-10 2012-01-19 Geräte- und Pumpenbau GmbH Dr. Eugen Schmidt Regelbare Kühlmittelpumpe und Verfahren zu deren Regelung
DE102008026218B4 (de) 2008-05-30 2012-04-19 Geräte- und Pumpenbau GmbH Dr. Eugen Schmidt Regelbare Kühlmittelpumpe
DE102008046424A1 (de) 2008-09-09 2010-03-11 Schaeffler Kg Regelbare Kühlmittelpumpe
CN102439317B (zh) 2009-04-30 2014-07-02 欧根·施密特博士仪器和泵制造有限责任公司 可切换的冷却剂泵
DE102010046450A1 (de) 2010-09-24 2012-03-29 Schaeffler Technologies Gmbh & Co. Kg Abdichtung für eine regelbare Kühlmittelpumpe
DE102010050261B3 (de) 2010-11-02 2012-05-03 Geräte- und Pumpenbau GmbH Dr. Eugen Schmidt Regelbare Kühlmittelpumpe
DE102010053510B4 (de) 2010-12-04 2014-01-23 Geräte- und Pumpenbau GmbH Dr. Eugen Schmidt Kühlmittelpumpe
US9096207B2 (en) 2010-12-31 2015-08-04 Cummins Inc. Hybrid vehicle powertrain cooling system
DE102011004172B3 (de) 2011-02-15 2012-03-01 Schwäbische Hüttenwerke Automotive GmbH Kühlmittelpumpe mit verstellbarem Fördervolumen
DE102011001090A1 (de) 2011-03-04 2012-09-06 Geräte- und Pumpenbau GmbH Dr. Eugen Schmidt Merbelsrod Regelbares Kühlsystem für ein Kraftfahrzeug, Kühlmittelpumpe hierfür, in der Kühlmittelpumpe verwendbares Flügelrad sowie Verfahren zum Regeln eines Kühlmittelflusses in einem derartigen Kühlsystem
DE102011076138A1 (de) * 2011-05-19 2012-11-22 Schaeffler Technologies AG & Co. KG Aktuatorik zur Verstellung einer regelbaren Kühlmittelpumpe
CN202117755U (zh) 2011-06-15 2012-01-18 中国汽车技术研究中心 不受发动机转速影响的发动机电控辅助冷却系统
DE102011079310A1 (de) 2011-07-18 2013-01-24 Schaeffler Technologies AG & Co. KG Kühlmittelpumpe für einen Kühlmittelkreislauf einer Brennkraftmaschine
DE102011079311A1 (de) 2011-07-18 2013-01-24 Schaeffler Technologies AG & Co. KG Kühlmittelpumpe für einen Kühlmittelkreiskreislauf einer Brennkraftmaschine
DE102011113040B3 (de) * 2011-09-09 2012-04-26 Geräte- und Pumpenbau GmbH Dr. Eugen Schmidt "Regelbare Kühlmittelpumpe"
DE102012204044A1 (de) 2012-03-15 2013-09-19 Schaeffler Technologies AG & Co. KG Regelbare Kühlmittelpumpe mit einem mehrteiligen modulartigen Aufbau
US9574485B2 (en) * 2012-10-19 2017-02-21 Pierburg Pump Technology Gmbh Mechanical coolant pump
DE102012223069A1 (de) 2012-12-13 2014-06-18 Bayerische Motoren Werke Aktiengesellschaft Kühlmittelkreislauf für eine Brennkraftmaschine
DE102013011209B3 (de) 2013-07-04 2014-01-23 Geräte- und Pumpenbau GmbH Dr. Eugen Schmidt Regelbare Kühlmittelpumpe
DE102013018205B3 (de) 2013-10-30 2014-06-18 Geräte- und Pumpenbau GmbH Dr. Eugen Schmidt Regelbare Kühlmittelpumpe
DE102013111939B3 (de) * 2013-10-30 2014-10-30 Pierburg Gmbh Kühlmittelpumpe für den Einsatz im KFZ-Bereich
DE102014110231B3 (de) 2014-07-21 2015-09-10 Nidec Gpm Gmbh Kühlmittelpumpe mit integrierter Regelung
DE102015109966B3 (de) * 2015-06-22 2016-06-16 Nidec Gpm Gmbh Kühlmittelpumpe mit integrierter Regelung
WO2016012379A1 (fr) 2014-07-21 2016-01-28 Nidec Gpm Gmbh Pompe à réfrigérant munie d'une régulation intégrée
DE102015114783B3 (de) 2015-09-03 2016-09-22 Nidec Gpm Gmbh Elektrische Kühlmittelpumpe mit strömungsgekühlter Steuerschaltung

Also Published As

Publication number Publication date
US11002281B2 (en) 2021-05-11
CN111051702A (zh) 2020-04-21
US20200340482A1 (en) 2020-10-29
WO2019042644A1 (fr) 2019-03-07
CN111051702B (zh) 2021-09-14
BR112019028100A2 (pt) 2020-07-28
DE102017120191B3 (de) 2018-12-06
EP3676498B1 (fr) 2021-06-09

Similar Documents

Publication Publication Date Title
EP2412955B1 (fr) Procédé de freinage moteur
EP2705279B1 (fr) Circuit hydraulique et son procédé de fonctionnement
DE602005000208T2 (de) Kraftstoffzufuhrsystem
EP2169233B1 (fr) Système de refroidissement pour véhicules dotés d'un moteur à combustion interne refroidi par du liquide
DE19652831B4 (de) Druckfluid-Speisesystem für die Versorgung von Hochdruck-Sammelleitungen
DE69109799T2 (de) Brennstoffregeleinrichtung für Gasturbine.
DE112008000978T5 (de) Hydraulische Pumpe mit variablem Durchfluss und Druck und verbesserter elektrischer Steuerung mit offenem Regelkreis
EP2307726B1 (fr) Pompe à cylindrée variable
DE3818241A1 (de) Turboladermotorsystem
DE102014214441B4 (de) Verfahren und Anordnung zum Verzögern eines Hydrostatischen Antriebs
DE102014218419A1 (de) Hydrostatischer Antrieb
EP1275852A2 (fr) Turbo-compresseur dans un moteur à combustion
WO1998021484A1 (fr) Systeme de soupape et procede de realisation
DE3824398C2 (de) Schmierölpumpe
EP3676498B1 (fr) Pompe à liquide de refroidissement pouvant être régulée pour un circuit de refoulement principal et un circuit de refoulement secondaire
EP0039375B1 (fr) Dispositif de contrôle dans une machine à ondes de pression à dynamique des gaz pour la suralimentation d'un moteur à combustion interne
EP2597317A1 (fr) Machine-outil et groupe moteur-pompe
DE4304403C2 (de) Regeleinrichtung für einen hydrostatischen Antrieb
DE102013217121A1 (de) Motorschmierungs-Steuersystem
DE10058032A1 (de) Hydraulische Steueranordnung
EP4127470B1 (fr) Pompe haute pression
DE19839579C1 (de) Einspritzsystem
DE4325600A1 (de) Aufgeladene Brennkraftmaschine mit mindestens zwei Abgasturboladern
EP1809507B1 (fr) Mecanisme d'entrainement hydrostatique
DE102018211094A1 (de) Verfahren zum Betreiben einer Brennkraftmaschine, Brennkraftmaschine und Kraftfahrzeug

Legal Events

Date Code Title Description
STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: UNKNOWN

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

Free format text: STATUS: THE INTERNATIONAL PUBLICATION HAS BEEN MADE

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

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

Free format text: STATUS: REQUEST FOR EXAMINATION WAS MADE

17P Request for examination filed

Effective date: 20200220

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 RS SE SI SK SM TR

AX Request for extension of the european patent

Extension state: BA ME

DAV Request for validation of the european patent (deleted)
DAX Request for extension of the european patent (deleted)
GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

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

Free format text: STATUS: GRANT OF PATENT IS INTENDED

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

INTG Intention to grant announced

Effective date: 20210408

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

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

Free format text: STATUS: THE PATENT HAS BEEN GRANTED

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 RS 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

Ref country code: AT

Ref legal event code: REF

Ref document number: 1400732

Country of ref document: AT

Kind code of ref document: T

Effective date: 20210615

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 502018005669

Country of ref document: DE

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: LT

Ref legal event code: MG9D

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

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: 20210609

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: 20210609

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: 20210609

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: 20210909

REG Reference to a national code

Ref country code: NL

Ref legal event code: MP

Effective date: 20210609

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: 20210609

Ref country code: RS

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: 20210609

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: 20210909

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: 20210609

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: 20210910

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

Ref country code: DE

Payment date: 20210712

Year of fee payment: 4

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: 20210609

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: 20210609

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: 20210609

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: 20210609

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: 20210609

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: 20210609

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: 20211011

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: 20210609

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

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: 20210609

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 502018005669

Country of ref document: DE

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: 20210609

REG Reference to a national code

Ref country code: BE

Ref legal event code: MM

Effective date: 20210731

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: LI

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

Effective date: 20210731

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: 20210609

Ref country code: CH

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

Effective date: 20210731

26N No opposition filed

Effective date: 20220310

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: 20210712

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: 20210609

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

Effective date: 20210609

Ref country code: IE

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

Effective date: 20210712

Ref country code: FR

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

Effective date: 20210809

Ref country code: BE

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

Effective date: 20210731

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 502018005669

Country of ref document: DE

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

Effective date: 20220712

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: 20220712

Ref country code: DE

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

Effective date: 20230201

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: 20210609

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

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: 20180712

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: 20210609

REG Reference to a national code

Ref country code: AT

Ref legal event code: MM01

Ref document number: 1400732

Country of ref document: AT

Kind code of ref document: T

Effective date: 20230712

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: 20210609

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: 20230712

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: 20230712

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: 20210609

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

Ref country code: AT

Payment date: 20260410

Year of fee payment: 5