EP2300718B1 - Regelbare kühlmittelpumpe - Google Patents

Regelbare kühlmittelpumpe Download PDF

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Publication number
EP2300718B1
EP2300718B1 EP09753548.8A EP09753548A EP2300718B1 EP 2300718 B1 EP2300718 B1 EP 2300718B1 EP 09753548 A EP09753548 A EP 09753548A EP 2300718 B1 EP2300718 B1 EP 2300718B1
Authority
EP
European Patent Office
Prior art keywords
pump
impeller
sleeve
piston
working
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.)
Not-in-force
Application number
EP09753548.8A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP2300718A2 (de
Inventor
Eugen Schmidt
Franz Pawellek
Eberhard Geissel
Dirk Hagen
Michael REXHÄUSER
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 EP2300718A2 publication Critical patent/EP2300718A2/de
Application granted granted Critical
Publication of EP2300718B1 publication Critical patent/EP2300718B1/de
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B23/00—Pumping installations or systems
    • F04B23/04—Combinations of two or more pumps
    • F04B23/08—Combinations of two or more pumps the pumps being of different types
    • F04B23/10—Combinations of two or more pumps the pumps being of different types at least one pump being of the reciprocating positive-displacement type
    • F04B23/106—Combinations of two or more pumps the pumps being of different types at least one pump being of the reciprocating positive-displacement type being an axial piston pump
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B23/00—Pumping installations or systems
    • F04B23/04—Combinations of two or more pumps
    • F04B23/08—Combinations of two or more pumps the pumps being of different types
    • F04B23/14—Combinations of two or more pumps the pumps being of different types at least one pump being of the non-positive-displacement type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D13/00—Pumping installations or systems
    • F04D13/12—Combinations of two or more pumps
    • 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 invention relates to a controlled via a pulley controllable coolant pump for internal combustion engines.
  • the cylinder head in order to bring the exhaust gas temperature as fast as possible to the desired level, during the cold start phase, the cylinder head should not be flowed through by coolant.
  • controllable coolant pumps are also described by the crankshaft of the internal combustion engine driven by pulleys, in which the impeller is shiftably driven (for example via a friction pairing) by the pump shaft.
  • the drive of the coolant pump is disengaged during cold start of the engine by means of these designs.
  • the respective friction clutch (with the wear-related function problems inherent in this type of clutch) is activated, i. E. the drive of the coolant pump is turned on.
  • hydraulically actuated actuators are also sensitive to temperature, as their dynamics at liquid temperatures below 0 ° C is significantly impaired.
  • the invention is therefore based on the object to develop a driven via a pulley controllable coolant pump (with valve slide), which eliminates the aforementioned disadvantages of the prior art, on the one hand by "zero leakage” ensures optimum heating of the engine and also on the other hand the engine warming can influence the engine temperature in continuous operation so accurately that the pollutant emission as well as the friction losses and the fuel consumption can be significantly reduced in the entire working range of the engine and even in unfavorable thermal boundary conditions, such as in the vicinity of the turbocharger, but also with very limited installation space for the coolant pump in the engine compartment with a very low drive power reliable actuation of the valve spool and even in case of failure of the control further functioning of the coolant pump (fail-safe) ensured, also by a manufacturing and assembly technology very simple, cost-effective, for different pump sizes " standardisable ", optimally exploiting the design space available in the engine compartment, always ensuring high reliability and reliability with high volumetric efficiency, requiring no factory air-free filling and
  • this object is achieved by a driven via a pulley controllable coolant pump for internal combustion engines according to the features of the independent claim of the invention.
  • FIG. 1 is the inventive, controllable coolant pump in a first embodiment with a split filter in the side view in section, with the position of the valve spool in its rear end position (ie in the working position "OPEN").
  • a pump shaft 4 driven by a pulley 3 is arranged on a pump housing 1, in a pump bearing 2, with an impeller 5 arranged in a rotationally fixed manner on the free, flow-side end of this pump shaft 4.
  • a pressure-actuated, spring-loaded by a return spring 6 valve spool with a rear wall 7 and an outflow of the impeller 5 variable overlapping outer cylinder 9 is arranged in the pump interior.
  • a shaft seal 11 is disposed between the impeller 5 and the pump bearing 2 in a seal holder 10.
  • a work housing 12 is arranged on the pump housing 1 in which a solenoid valve 13 is arranged with an inlet opening 14. Adjacent to this inlet opening 14, a pressure chamber 15 is arranged pump shaft side in the working housing 12 into which a pressure channel 16 opens, which connects the pressure chamber 15 with an annular channel 17.
  • This annular channel 17 is arranged according to the invention in the pump housing 1 in a wellgelrad nurse the seal holder 10 opposite Sleeve receptacle 18 rotationally symmetrical to the axis of rotation of the shaft 4 incorporated.
  • the pump housing 1 and the working housing 12 are made of one piece.
  • flow openings 23 are arranged to the annular channel 17 near the bottom.
  • the restoring spring 6 is arranged between the wall plate 26 and the rear wall 7 of the valve slide resting against the annular piston 29.
  • an edge web 30 is arranged, which stabilizes the rear wall 7 of the valve spool during its working stroke in the position.
  • a bypass seal 31 is arranged, which prevents a pressure build-up between the wall plate 26 and the rear wall 7 of the valve slide in "closed" valve spool.
  • a swashplate 32 is arranged rigidly on the impeller 5 on the pump housing side and a suction groove 33 is made in its "sinking region", wherein the transition region into the "riser region” and the entire “riser region” of the swashplate 32 are planar.
  • the impeller 5 is in the FIG. 2 shown as item in the back view.
  • the FIG. 3 shows the impeller 5 of the controllable coolant pump according to the invention in a partial section according to the FIG. 2 at AA.
  • a deep-drawn precision cylinder sleeve is pressed into the insertion bore 36 of the pump housing 1.
  • a sealing ring 52 is arranged to seal the cylinder sleeve 37, which prevents bypass leakage.
  • the wall of the arranged in the rear wall 7 of the valve slide through opening 35 does not touch the jacket of the cylinder sleeve 37, so that the valve spool along the cylinder sleeve 37 is freely movable.
  • FIG. 4 shows a plan view of the integrated in the cylinder sleeve 37 axial piston pump 61, from the direction A, according to FIG. 5 ,
  • FIG. 5 In the assigned FIG. 5 is the cylinder sleeve 37 (according to FIG. 4 ) with the components of the integrated axial piston pump 61 in section in the side view.
  • a valve cage 40 is arranged with a valve spring 41 and a valve spring 41 pressed by this valve spring 41 in the region of the discharge port 39 against the cylinder sleeve bottom 38 valve disc 42, and that in the valve cage 40 more Passage openings 43 are located.
  • a working spring 44 is arranged in the cylinder sleeve 37, against which a working piston 45 with a flow-through bore 46 rests on the impeller side.
  • annular groove 53 is introduced into the outer cylinder of the working piston 45 in a piston ring 54th is arranged, which serves an optimal sealing effect with minimized friction losses.
  • a sliding shoe 47 is arranged with a passage bore 48, which is introduced in the associated region of the suction groove 33 and is adjacent to the throughflow bore 46 of the working piston 45.
  • the contact region 55 between the sliding shoe 47 and the working piston 45 is formed as a ball joint, so that the sliding shoe 47 always rests flat on the associated contact surface of the swash plate.
  • the sliding block 47 is fastened by means of a clamping hook 57 provided with clamping sleeve 57 on the working piston 45, wherein in the clamping sleeve a sleeve passage bore 58 is arranged.
  • the stroke per revolution is a maximum of one millimeter, since due to the arrangement according to the invention very low flow rates sufficient for an accurate actuation / displacement of the valve spool.
  • the throughflow bore 46 (or the sleeve passage bore 58 of the throughflow bore 46 arranged in the sliding shoe 47 takes place arranged clamping sleeve 57 therethrough, a defined inventive inflow of the coolant via the suction groove 33 into the piston chamber 59 of the cylinder sleeve 37th
  • the incorporated into the swash plate 32 suction groove 33 is used according to the invention in conjunction with the sliding block 47 as a gap filter, so that at the same time a filtering of the coolant is effected during the inflow.
  • the arrangement according to the invention is resistant to particles entrained by the coolant (such as, for example, chips or grains of sand).
  • the suction groove 33 is incorporated 0.1 mm deep in the swash plate 32.
  • valve spring 41 valve disc 42 is raised and at the same time the sucked coolant through the arranged at the edge of the valve disc 42 holes 60 through the arranged in the valve basket 40 passage openings 43 through into the pressure channel 16 pressed.
  • the outlet opening 49 arranged on the magnetic valve 13 is arranged in the working housing 12 according to the invention an outflow groove 50. It is essential to the invention that this outflow groove 50 is connected to the pump interior 8 via a return flow bore 51 leading from the working housing 12 into the pump housing 1.
  • the solenoid valve 13 is normally open.
  • the working piston 45 of the piston pump conveys at "open" solenoid valve 13, the refrigerant pressure via the outlet opening 49 of the solenoid valve 13 back into the pump interior.
  • the pumped from the piston pump coolant enters the annular channel 17 and is pressed from there via the flow openings 23 into the annular piston working sleeve 19.
  • the pressure in the pressure channel can be precisely controlled by means of the solenoid valve, thus realizing a defined movement of the valve spool along the outer edge of the impeller, which in turn allows the engine temperature to be accurately influenced in continuous operation, so that in the entire engine operating range, both the pollutant emissions as well as the friction losses and fuel consumption can be significantly reduced.
  • the solution according to the invention due to the arrangement of an integrated in the coolant pump housing and at the same time cooled by the coolant in the coolant pump housing solenoid valve ensures optimum cooling with minimal construction volume ,
  • the solution according to the invention enables a reliable actuation of the valve spool with a very low drive power.
  • FIG. 6 shows this second, equipped with a special centrifugal separator according to the invention embodiment in a three-dimensional representation.
  • a working housing 12 with a solenoid valve 13 is arranged on the pump housing 1.
  • FIG. 7 shows the controllable coolant pump according to the invention in the side view, in a section at AA, according to FIG. 6 ,
  • This second embodiment of the controllable coolant pump according to the invention is again provided with a pump housing 1, a pump shaft 4 mounted in / on the pump housing 1, driven by a pulley 3 pump shaft 4, on a free, flow-side end of this pump shaft 4 rotatably mounted impeller 5, a pressure-actuated, spring-loaded by a return spring 6, provided with a rear wall 7 and a flow area of the impeller 5 variably overlapping outer cylinder 9, arranged in the pump interior 8 valve spool and a in Pump housing 1 between the impeller 5 and the pump bearing 2 in a seal receiving 10 arranged shaft seal 11 equipped.
  • this design is also characterized in that a solenoid valve 13 with an inlet opening 14 is arranged in the working housing 12 arranged on the pump housing 1, whereby this inlet opening 14 is also arranged adjacently to a pump chamber 15 in the working housing 12, into which a pressure channel 16 opens.
  • a solenoid valve 13 with an inlet opening 14 is arranged in the working housing 12 arranged on the pump housing 1, whereby this inlet opening 14 is also arranged adjacently to a pump chamber 15 in the working housing 12, into which a pressure channel 16 opens.
  • an annular piston working sleeve 19 is arranged with a sealing web 20 and a bottom 21 in which the pump shaft 4 rotates freely and in the outer cylinder 22 near the bottom 21 through-flow openings 23 are arranged to the annular channel 17, wherein the end on the erielrad workedem on the Outer cylinder 22 clearly superior inner cylinder 24 of the annular piston working sleeve 19 a position securing sleeve 25 is arranged with a rigidly arranged on this wall plate 26 frictionally, and spaced from the bottom 21 of the annular piston working sleeve 19, spaced about the diameter of the flow openings 23, in the annular piston working sleeve 19 slidably disposed a profile seal 27 is the flywheel side positively connected to a provided with a contact web 28 annular piston 29, at the coperad Koner end wall, the rear wall 7 of the valve spool is positively and / or non-positively disposed
  • a bypass seal 31 is arranged at the outer edge of the wall plate 26 so that it prevents pressure build-up between the wall plate 26 and the rear wall of the valve spool in any position of the valve spool and thereby displacement of the valve spool against the in the FIGS. 1 to 5 shown solution again much more precise (more sensitive) allows.
  • a swash plate 32 is arranged on the impeller 5 in this design pump housing side is rigidly mounted in the "sinking” a suction groove 33, wherein the transition region in the “riser” as well as the entire “riser” of the swash plate 32 is planar ,
  • Characteristic in this context is that on the pump housing 1 more the pump housing 1 in the direction of impeller 5 towering domes, a pumping dome 63, one or more Wandusionnbefest Trentsdome 64 and a remindströmdom 65 are arranged, and that in the rear wall 7 in the region of these dome assigned through openings 35 are arranged, which ensure a "free" movability of the valve spool.
  • the wall plate 26 is fixed to the Wandusionnbefest onlysdomen 64 of the pump housing 1 by means of fasteners 71, and that in the fixed via the Wandusionnbefest onlysdome 64 fixed to the pump housing 1 wall plate 26, on the one hand centric to that in the Swash plate 32 arranged suction groove 33 has a through-hole 34 and the bore axis in the pumping end 63 of the pump housing 1 opening into the pressure channel 16 Einsteckbohrung 36 is arranged, and on the other hand a Wandusionn miclassbohrung 73 is arranged, which centric to the bore axis arranged in remindströmdom 65 remindströmbohrung 51 is.
  • a pump dome seal 70 is arranged, which avoids leaks between the adjacent components there. It is also advantageous, although at staströmdom 65 as in the FIG. 8 is shown, in the outlet region of the return flow bore 51, a remindströmdomdichtung 74 is disposed between the return flow bore 51 and disposed in the wall plate 26 Wandusionn biobohrung 73 remindströmdomdichtung 74, which avoids leakage between the adjacent components there.
  • a cylindrical sleeve 37 with an integrated in this cylinder sleeve 37 axial piston pump 61 is arranged in the insertion bore 36 in the pumping dome 63 of the pump housing 1 form and locks.
  • FIG. 9 is this cylinder sleeve 37 according to FIG. 7 shown in section in the side view with the integrated in the cylinder sleeve 37 components of the axial piston pump 61 used in this embodiment.
  • an outlet opening 39 is arranged in the area of the cylinder sleeve bottom 38 of the cylinder sleeve 37, and in the area of the cylinder sleeve bottom 38 outside the cylinder sleeve 37 a valve cage 40 with a valve spring 41 and one of this valve spring 41 in the area of the outlet opening 39 the cylinder sleeve bottom 38 pressed valve disc 42 is arranged, with one / more passage opening / s 43 is / are located in the valve cage 40, and arranged in the cylinder sleeve 37 as a further assembly of the axial piston pump 61 is a working spring 44 is on the impeller side of the associated provided with a flow-through bore 46 working piston 45 is present.
  • the stroke per revolution is at most two millimeters, since due to the inventive arrangement even small flow rates sufficient for accurate actuation / displacement of the valve spool.
  • FIG. 10 now shows the controllable coolant pump according to the invention according to FIG. 7 with the centrifugal separator according to the invention in section at CC.
  • a suction groove 33 incorporated into the swashplate 32 approximately 0.6 mm deep is covered by means of a centrifugal separator 62 which covers the suction groove 33 and is arranged between the swashplate 32 and the sliding shoe 47.
  • centrifugal separator 62 is formed by a thin-walled circular disk arranged in the region of the suction groove 33, in which as in FIG. 10 shown, in the region of the suction groove 33 a plurality of laser bores 68 are arranged.
  • approximately 4000 laser bores are arranged in the region of the suction groove 33 in the centrifugal separator 62.
  • the thickness of the annular disk of the centrifugal separator 62 according to the invention is 0.3 mm, and the laser bores 68 used in this embodiment have a conical cross section.
  • the smallest diameter of these conical laser bores 68 is 0.1 mm and, according to the invention, is arranged on the side of the centrifugal separator 62 facing the sliding block 47.
  • the assigned and the suction groove 33 facing the largest diameter of these conical laser bores 68 is 0.15 mm in the present embodiment.
  • the centrifugal separator 62 firstly effects a filtering of the coolant flowing into the suction groove 33, on the one hand as “centrifugal separator", since the foreign body (such as shavings, grains of sand, or the like) that is entrained by the cooling medium acts on it Centrifugal force from the peripheral speed of the impeller 5 (with which the centrifugal separator 62 rotates) is substantially greater in the region of the laser bores 68, compared with the "suction force" acting on the foreign bodies from the inflow velocity into the laser bores 68.
  • centrifugal separator 62 acts as a "baffle separator", since all not exactly the laser bore 68 impinging foreign body bounce off of the arranged between the laser bores 68 "base material of the centrifugal separator" 62 and then additionally rejected by the centrifugal force effect.
  • each laser bore 68 flows twice (once into the suction groove 33 and then over the sliding shoe 47 out of the suction groove 33) with each revolution of the impeller 5 and is additionally flushed free.
  • the arrangement according to the invention causes (at an engine speed of, for example, 3000 rpm at which the laser bore area of the centrifugal separator 62 fifty times per Second with all the aforementioned effects and a very high suction pressure is exceeded as a result of the sealed laser bores) a cleaning effect very close to ultrasonic cleaning, whereby the centrifugal separator 62 according to the invention cleans even under extreme conditions and also already formed crystals go back into solution.
  • This arrangement according to the invention allows compared to the embodiment presented in the first embodiment, a significantly higher "Einstömvolumenstrom", is resistant to the particles entrained by the coolant and also ensures a very long service life with maximum reliability.
  • the sliding shoe 47 During its subsequent movement along the "rising region" of the swash plate 32, the sliding shoe 47 then presses the working piston 45 into the piston chamber 59 of the cylinder sleeve 37.
  • valve spring 41 valve disc 42 is raised and at the same time the sucked coolant through the arranged at the edge of the valve disc 42 holes 60 through the arranged in the valve basket 40 passage openings 43 through into the pressure channel 16 is pressed ( FIG. 7 ).
  • FIG. 8 is the inventive, controllable coolant pump from the FIG. 6 now shown in the side view in section at BB.
  • FIG. 8 This sectional view according to FIG. 8 shows that the solenoid valve 13, an outlet opening 49 is arranged, which in the working housing 12 adjacent to the working housing 12 in the pump housing 1 leading remindströmbohrungen 51 are arranged, which connect the outlet opening 49 with the pump interior 8.
  • the solenoid valve 13 is normally open.
  • the working piston 45 of the piston pump conveys the cooling liquid without pressure via the outlet opening 49 of the solenoid valve 13 back into the pump interior 8 in the case of an "open" solenoid valve 13.
  • the pressure in the pressure channel 16, in the annular channel 17 and connected to the annular channel 17 space of the annular piston working sleeve 19 is increased continuously.
  • the delivered from the axial piston pump 61 coolant passes into the annular channel 17 and is pressed from there via the flow openings 23 into the annular piston working sleeve 19.
  • the coolant thus pressed in causes a defined (via the solenoid valve 13 adjustable pressurization of the profile seal 27 and thus a pressurization of the spring-loaded annular piston 29, which thereby can be moved exactly translational.
  • the pressure in the pressure channel can be precisely controlled by means of the solenoid valve 13 and a defined process of the valve spool along the outer edge of the impeller 5 can be realized, which in turn allows the engine temperature to be influenced precisely in continuous operation that both the pollutant emissions as well as the friction losses and the fuel consumption can be significantly reduced in the entire working range of the engine.
  • the solution according to the invention ensures optimum cooling with minimized construction volume due to the arrangement of a solenoid valve 13 integrated in the coolant pump housing and at the same time cooled by the coolant in the coolant pump housing.
  • the solution according to the invention enables a reliable actuation of the valve spool with a very low drive power.
  • Both embodiments presented in the embodiments of the solution according to the invention are each characterized by a production and Assembly technology very simple, cost-effective, "standardizable" for different pump sizes, optimally exploiting the available space in the engine compartment space design and requires no factory air-free filling.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Reciprocating Pumps (AREA)
  • Details Of Reciprocating Pumps (AREA)
  • Supercharger (AREA)
EP09753548.8A 2008-05-30 2009-05-27 Regelbare kühlmittelpumpe Not-in-force EP2300718B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102008026218A DE102008026218B4 (de) 2008-05-30 2008-05-30 Regelbare Kühlmittelpumpe
PCT/DE2009/000751 WO2009143832A2 (de) 2008-05-30 2009-05-27 Regelbare kühlmittelpumpe

Publications (2)

Publication Number Publication Date
EP2300718A2 EP2300718A2 (de) 2011-03-30
EP2300718B1 true EP2300718B1 (de) 2018-07-25

Family

ID=41253984

Family Applications (1)

Application Number Title Priority Date Filing Date
EP09753548.8A Not-in-force EP2300718B1 (de) 2008-05-30 2009-05-27 Regelbare kühlmittelpumpe

Country Status (7)

Country Link
US (1) US8297942B2 (zh)
EP (1) EP2300718B1 (zh)
JP (1) JP5200163B2 (zh)
CN (1) CN102046982B (zh)
BR (1) BRPI0909834B1 (zh)
DE (1) DE102008026218B4 (zh)
WO (1) WO2009143832A2 (zh)

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DE102011012827B3 (de) 2011-03-02 2012-04-19 Geräte- und Pumpenbau GmbH Dr. Eugen Schmidt Vorrichtung u. Verfahren zur definierten Längsverschiebung einer in einer Antriebswelle mitdrehenden Verstellvorrichtung
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DE102015109966B3 (de) * 2015-06-22 2016-06-16 Nidec Gpm Gmbh Kühlmittelpumpe mit integrierter Regelung
DE102015000805B3 (de) 2015-01-22 2016-01-21 Nidec Gpm Gmbh Regelbare Kühlmittelpumpe
DE102015119092B4 (de) 2015-11-06 2019-03-21 Pierburg Gmbh Verfahren zur Regelung einer mechanisch regelbaren Kühlmittelpumpe für eine Verbrennungskraftmaschine
DE102015119098B4 (de) 2015-11-06 2019-03-21 Pierburg Gmbh Regelanordnung für eine mechanisch regelbare Kühlmittelpumpe einer Verbrennungskraftmaschine
DE102015119089B4 (de) * 2015-11-06 2019-03-21 Pierburg Gmbh Kühlmittelpumpe für eine Verbrennungskraftmaschine
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WO2009143832A8 (de) 2010-05-27
JP2011522145A (ja) 2011-07-28
EP2300718A2 (de) 2011-03-30
US8297942B2 (en) 2012-10-30
WO2009143832A3 (de) 2010-01-21
US20100284832A1 (en) 2010-11-11
DE102008026218A1 (de) 2009-12-03
JP5200163B2 (ja) 2013-05-15
CN102046982A (zh) 2011-05-04
BRPI0909834B1 (pt) 2019-10-22
BRPI0909834A2 (pt) 2015-10-06
WO2009143832A2 (de) 2009-12-03
DE102008026218B4 (de) 2012-04-19
CN102046982B (zh) 2014-08-20

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