WO2019042644A1 - Regelbare kühlmittelpumpe für haupt- und nebenförderkreislauf - Google Patents
Regelbare kühlmittelpumpe für haupt- und nebenförderkreislauf Download PDFInfo
- Publication number
- WO2019042644A1 WO2019042644A1 PCT/EP2018/068958 EP2018068958W WO2019042644A1 WO 2019042644 A1 WO2019042644 A1 WO 2019042644A1 EP 2018068958 W EP2018068958 W EP 2018068958W WO 2019042644 A1 WO2019042644 A1 WO 2019042644A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- pump
- valve
- pressure
- circuit
- hydraulic
- Prior art date
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
- F04D15/0027—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
- 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
- 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
Description
Claims
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US16/643,009 US11002281B2 (en) | 2017-09-01 | 2018-07-12 | Controllable coolant pump for a main delivery circuit and a secondary delivery circuit |
BR112019028100-2A BR112019028100A2 (pt) | 2017-09-01 | 2018-07-12 | bomba de líquido de refrigeração controlável para um circuito de entrega principal e um circuito de entrega secundário |
CN201880055517.7A CN111051702B (zh) | 2017-09-01 | 2018-07-12 | 用于主和次级输送回路的可控冷却剂泵 |
EP18740810.9A EP3676498B1 (de) | 2017-09-01 | 2018-07-12 | Regelbare kühlmittelpumpe für haupt- und nebenförderkreislauf |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102017120191.2 | 2017-09-01 | ||
DE102017120191.2A DE102017120191B3 (de) | 2017-09-01 | 2017-09-01 | Regelbare Kühlmittelpumpe für Haupt- und Nebenförderkreislauf |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2019042644A1 true WO2019042644A1 (de) | 2019-03-07 |
Family
ID=62916672
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/EP2018/068958 WO2019042644A1 (de) | 2017-09-01 | 2018-07-12 | Regelbare kühlmittelpumpe für haupt- und nebenförderkreislauf |
Country Status (6)
Country | Link |
---|---|
US (1) | US11002281B2 (de) |
EP (1) | EP3676498B1 (de) |
CN (1) | CN111051702B (de) |
BR (1) | BR112019028100A2 (de) |
DE (1) | DE102017120191B3 (de) |
WO (1) | WO2019042644A1 (de) |
Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102010050261B3 (de) | 2010-11-02 | 2012-05-03 | Geräte- und Pumpenbau GmbH Dr. Eugen Schmidt | Regelbare Kühlmittelpumpe |
WO2013034126A1 (de) * | 2011-09-09 | 2013-03-14 | Geräte- und Pumpenbau GmbH Dr. Eugen Schmidt | Regelbare kühlmittelpumpe |
DE102015109966B3 (de) * | 2015-06-22 | 2016-06-16 | Nidec Gpm Gmbh | Kühlmittelpumpe mit integrierter Regelung |
Family Cites Families (30)
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 |
US8814497B2 (en) | 2009-04-30 | 2014-08-26 | Geraete- Und Pumpenbau Gmbh Dr. Eugen Schmidt | Switchable coolant pump |
DE102010046450A1 (de) | 2010-09-24 | 2012-03-29 | Schaeffler Technologies Gmbh & Co. Kg | Abdichtung für eine 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 |
DE102012204044A1 (de) | 2012-03-15 | 2013-09-19 | Schaeffler Technologies AG & Co. KG | Regelbare Kühlmittelpumpe mit einem mehrteiligen modulartigen Aufbau |
EP2909456B1 (de) | 2012-10-19 | 2016-10-05 | Pierburg Pump Technology GmbH | Mechanische kühlmittelpumpe |
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 |
WO2016012379A1 (de) | 2014-07-21 | 2016-01-28 | Nidec Gpm Gmbh | Kühlmittelpumpe mit integrierter regelung |
DE102014110231B3 (de) | 2014-07-21 | 2015-09-10 | Nidec Gpm Gmbh | Kühlmittelpumpe mit integrierter Regelung |
DE102015114783B3 (de) | 2015-09-03 | 2016-09-22 | Nidec Gpm Gmbh | Elektrische Kühlmittelpumpe mit strömungsgekühlter Steuerschaltung |
-
2017
- 2017-09-01 DE DE102017120191.2A patent/DE102017120191B3/de not_active Expired - Fee Related
-
2018
- 2018-07-12 US US16/643,009 patent/US11002281B2/en active Active
- 2018-07-12 EP EP18740810.9A patent/EP3676498B1/de active Active
- 2018-07-12 WO PCT/EP2018/068958 patent/WO2019042644A1/de unknown
- 2018-07-12 CN CN201880055517.7A patent/CN111051702B/zh not_active Expired - Fee Related
- 2018-07-12 BR BR112019028100-2A patent/BR112019028100A2/pt not_active Application Discontinuation
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102010050261B3 (de) | 2010-11-02 | 2012-05-03 | Geräte- und Pumpenbau GmbH Dr. Eugen Schmidt | Regelbare Kühlmittelpumpe |
WO2013034126A1 (de) * | 2011-09-09 | 2013-03-14 | Geräte- und Pumpenbau GmbH Dr. Eugen Schmidt | Regelbare kühlmittelpumpe |
DE102015109966B3 (de) * | 2015-06-22 | 2016-06-16 | Nidec Gpm Gmbh | Kühlmittelpumpe mit integrierter Regelung |
Also Published As
Publication number | Publication date |
---|---|
EP3676498A1 (de) | 2020-07-08 |
US11002281B2 (en) | 2021-05-11 |
CN111051702B (zh) | 2021-09-14 |
EP3676498B1 (de) | 2021-06-09 |
DE102017120191B3 (de) | 2018-12-06 |
BR112019028100A2 (pt) | 2020-07-28 |
US20200340482A1 (en) | 2020-10-29 |
CN111051702A (zh) | 2020-04-21 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
EP2705279B1 (de) | Hydraulikkreis, verfahren zum betreiben | |
EP2412955B1 (de) | Verfahren zur Motorbremsung | |
DE602005000208T2 (de) | Kraftstoffzufuhrsystem | |
EP2169233B1 (de) | Kühlsystem für fahrzeuge mit flüssigkeitsgekühlter brennkraftmaschine | |
DE19652831B4 (de) | Druckfluid-Speisesystem für die Versorgung von Hochdruck-Sammelleitungen | |
DE112008000978T5 (de) | Hydraulische Pumpe mit variablem Durchfluss und Druck und verbesserter elektrischer Steuerung mit offenem Regelkreis | |
EP2307726B1 (de) | Verstellpumpe mit einem mengenregler und einem druckventil. | |
EP1275852A2 (de) | Abgasturbolader in einer Brennkraftmaschine | |
DE102014214441B4 (de) | Verfahren und Anordnung zum Verzögern eines Hydrostatischen Antriebs | |
EP0935713A1 (de) | Ventilanordnung und verfahren zur ansteuerung einer derartigen ventilanordnung | |
DE3824398C2 (de) | Schmierölpumpe | |
EP0039375B1 (de) | Steuerungseinrichtung in einer gasdynamischen Druckwellenmaschine zur Aufladung von Verbrennungsmotoren | |
EP3676498B1 (de) | Regelbare kühlmittelpumpe für haupt- und nebenförderkreislauf | |
EP2597317A1 (de) | Werkzeugmaschine und Motorpumpenaggregat | |
DE4304403C2 (de) | Regeleinrichtung für einen hydrostatischen Antrieb | |
DE19738502A1 (de) | System zur Hochdruckerzeugung | |
DE4015055B3 (de) | Brennstoffregelsystem für die Nachbrenner eines Gasturbinentriebwerks und Regelventile dafür | |
WO2021224386A1 (de) | Ventil mit einem hybridem antrieb, elektrisch und pneumatisch | |
DE19839579C1 (de) | Einspritzsystem | |
DE10058032A1 (de) | Hydraulische Steueranordnung | |
DE4325600A1 (de) | Aufgeladene Brennkraftmaschine mit mindestens zwei Abgasturboladern | |
EP1809507B1 (de) | Hydrostatischer antrieb | |
DE102015008135A1 (de) | Sicherheitsventil und Kraftstoffeinspritzsystem mit einem solchen | |
DE19605992A1 (de) | Hydraulische Steueranordnung, insbesondere für ein mobiles Arbeitsgerät | |
DE102020132336A1 (de) | Kompressorsystem |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
121 | Ep: the epo has been informed by wipo that ep was designated in this application |
Ref document number: 18740810 Country of ref document: EP Kind code of ref document: A1 |
|
REG | Reference to national code |
Ref country code: BR Ref legal event code: B01A Ref document number: 112019028100 Country of ref document: BR |
|
ENP | Entry into the national phase |
Ref document number: 2018740810 Country of ref document: EP Effective date: 20200401 |
|
ENP | Entry into the national phase |
Ref document number: 112019028100 Country of ref document: BR Kind code of ref document: A2 Effective date: 20191227 |