EP3371463A1 - Système de régulation d'une pompe à liquide de refroidissement à régulation mécanique d'un moteur à combustion interne - Google Patents

Système de régulation d'une pompe à liquide de refroidissement à régulation mécanique d'un moteur à combustion interne

Info

Publication number
EP3371463A1
EP3371463A1 EP16785429.8A EP16785429A EP3371463A1 EP 3371463 A1 EP3371463 A1 EP 3371463A1 EP 16785429 A EP16785429 A EP 16785429A EP 3371463 A1 EP3371463 A1 EP 3371463A1
Authority
EP
European Patent Office
Prior art keywords
control
pump
coolant pump
flow
internal combustion
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP16785429.8A
Other languages
German (de)
English (en)
Other versions
EP3371463B1 (fr
Inventor
Stephan Zielberg
Michael-Thomas Benra
Michael Sanders
Stefan Rothgang
Andreas Burger
Sven Nigrin
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.)
Pierburg GmbH
Original Assignee
Pierburg 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 Pierburg GmbH filed Critical Pierburg GmbH
Publication of EP3371463A1 publication Critical patent/EP3371463A1/fr
Application granted granted Critical
Publication of EP3371463B1 publication Critical patent/EP3371463B1/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
    • F04D15/0027—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
    • F01P5/00—Pumping cooling-air or liquid coolants
    • F01P5/10—Pumping liquid coolant; Arrangements of coolant pumps
    • 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
    • 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
    • F01P2005/105—Using 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 control arrangement for a mechanically controllable coolant pump of an internal combustion engine with an adjustable control slide, via which a flow cross section of an annular gap between an outlet of adeffenpumpenterrorisms and a surrounding conveyor channel is controllable, a control pump, via which a hydraulic pressure can be generated, a first pressure chamber of the A control slide, which is formed on a first axial side of the control slide and a solenoid valve having two valve seats and three flow ports and a closing member which is connected to an armature of the solenoid valve and axially movable, wherein the first flow port is fluidly connected to an outlet of the control pump and the second flow connection is fluidically connected to the first pressure chamber of the control slide.
  • Such control arrangements for coolant pumps are used in internal combustion engines to control the amount of subsidized coolant in order to prevent overheating of the internal combustion engine.
  • the drive of these pumps is usually via a belt or chain drive, so that thedeffenpumpenrad is driven by the speed of the crankshaft or a fixed ratio to the speed of the crankshaft.
  • the pumped coolant quantity is to be adapted to the coolant requirement of the internal combustion engine or of the motor vehicle.
  • the cold running phase should of the engine are shortened. This is done, inter alia, by throttling or completely shutting off the coolant flow during this phase.
  • control slide also takes place in different ways.
  • a hydraulic adjustment of the slide has proven. This is usually done via an annular piston chamber or otherwise executed pressure chamber which is filled with a hydraulic fluid to move when filling the slide on the coolant pump impeller.
  • a return of the control slide is done by opening the pressure chamber to an outlet, which is usually done via a 2/2-way solenoid valve and under the action of a spring, which provides the force to return the slider.
  • control arrangements In order not to have to provide the process of the control slide coolant amount on additional conveyor units, such as additional piston / cylinder units or compress other hydraulic fluids for actuation, control arrangements have become known in which a necessary pressure generating control pump on the drive shaft Coolant pump is arranged, which serves to adjust the slide accordingly.
  • control pumps are designed, for example, as side channel pumps or servo pumps.
  • a control arrangement for a mechanically driven, controllable coolant pump with a control pump, which generates a pressure for displacement of a control slide is known from DE 10 2012 207 387 AI.
  • a pressure side of the control pump is closed by a 3/2-way valve in a first position and a suction side of the pump connected to the cooling circuit and the slider and connected in a second position, the pressure side with the slide and the suction side with the cooling circuit.
  • a spring which may possibly be waived by a reset of the pump should be made by the resulting negative pressure on the suction port.
  • the first flow connection of the valve to the pressure chamber the second flow connection to the outlet of the control pump and the third flow connection to the inlet of the control pump.
  • a detailed channel and flow guidance of the control arrangement is not disclosed.
  • the flow guides shown schematically are technically feasible in modern internal combustion engines only with increased effort and space requirements.
  • a quick emptying of the piston chamber is not possible because the emptying takes place to the inlet of the control pump, which builds up a pressure in the entire channel, which acts as a back pressure in the piston chamber.
  • a provision of the slide in its maximum flow rate of the coolant pump locking position should possible without use a force acting on the control slide compression spring can be done. Furthermore, a variable control of the coolant flow should be possible if possible.
  • the third flow port is fluidly connected to an inlet of the coolant pump, wherein the first valve seat between the first flow port and the second flow port is formed and the second valve seat is formed between the second flow port and the third flow port, either a connection between the Pressure chamber and the inlet of the coolant pump are made, whereby the coolant there existing quickly sucked off and thus the pressure in the pressure chamber can be quickly degraded or a connection from the outlet of the control pump to the pressure chamber are made, whereby a pressurization of the pressure chamber and thus of the control slide , Thus, a short-term adjustment of the control slide is made possible by switching the solenoid valve.
  • the solenoid valve preferably has a flow housing in which the closing member is axially movable between the two valve seats and an electromagnetic actuator with a core, flux guide elements, a winding arranged on a coil carrier and the axially movable armature.
  • the closing member only has to travel short distances, whereby the switching times are reduced.
  • At least the flow housing of the solenoid valve is arranged in a receiving opening of a housing part of the coolant pump.
  • the solenoid valve is arranged in close proximity to the control pump, whereby the length of the lines is reduced, which also leads to a shortening of the switching times of the control arrangement.
  • little space is needed and the installation is simplified because the entire control arrangement can be pre-assembled with the coolant pump and inserted into the outer housing.
  • a first channel is formed in the housing part, via which the first pressure chamber is connected to the second flow connection. Additional lines are omitted. Instead, extremely short connections are created for faster switching times.
  • a second channel is formed, which is on the one hand connected to the first flow port of the solenoid valve and on the other hand continues in the control pump housing to the outlet of the control pump.
  • a third channel is preferably formed in the housing part, which is connected on the one hand to the third flow port of the solenoid valve and on the other hand extends into a radially inner passage opening of the housing part, which continues in the interior of the control pump housing and projects through the drive shaft of the coolant pump, wherein in the coolant pump impeller, an axial bore is formed, which leads to the inlet of the coolant pump.
  • a channel is formed in the region of an inlet of the control pump, via which a second pressure chamber is fluidically connected to the flow channel of the control pump, so that the coolant pump is constructed without additional, a continuous force applying means, such as compression springs and the like. This reduces the required control forces, which again switching the control arrangement with very short reaction times is possible.
  • the closing member of the solenoid valve is arranged on a valve rod, wherein a closing surface at a first axial end of the closing member is associated with the first valve seat and a closing surface is associated with the second valve seat at the opposite axial end.
  • the axial bearing of the closing member on the respective valve seat leads to a dense, almost leak-free closure of the respective flow cross-section. For this purpose, only a double-loaded locking member is required, whereby the structure of the solenoid valve is also facilitated.
  • the solenoid valve is preferably designed as a proportional valve. This allows a continuous control of the valve opening, so that the control slide is movable in intermediate positions and thus the coolant flow can be completely controlled. These valves had a long service life, since the high-frequency impingement of the valve body on the valve seat is eliminated.
  • the solenoid valve is variable clocked controlled.
  • Such a controlled servo valve is more expensive to manufacture, but allows an even more accurate Rules of the desired opening cross sections, so that even more accurate control of the position of the control slide is possible.
  • Figure 1 shows a side view of a coolant pump with inventive control arrangement in a sectional view.
  • FIG. 2 shows a side view of the coolant pump from FIG. 1 in a cut representation rotated relative to FIG.
  • FIG. 3 shows a representation, enlarged to FIG. 1, of a 3/2-way electromagnetic valve of a control arrangement according to the invention in a sectional representation.
  • the illustrated coolant pump 11 consists of an outer housing 10, in which a spiral conveying channel 12 is formed, in which a coolant is sucked in via an axial inlet 14 likewise formed in the outer housing 10, which coolant flows via the delivery channel 12 to a tangential pump outlet 16 formed in the outer housing 10 and is conveyed into a cooling circuit of the internal combustion engine.
  • a coolant pump impeller 20 is fixed radially inside the conveying channel 12 on a drive shaft 18, which serves as Radialpumpenrad is formed by the rotation of the promotion of the coolant takes place in the conveying channel 12.
  • the drive of the coolant pump impeller 20 via a belt 22 which engages in a pulley 24 which is secured to the coolant pump impeller 20 opposite axial end of the drive shaft 18.
  • the pulley 24 is supported by a double-row ball bearing 26, which is pressed onto a stationary housing part 28, which is fastened to the outer housing 10 with the interposition of a seal 30.
  • the housing part 28 has an annular projection 32, which is fitted into a corresponding receptacle of the outer housing 10.
  • a control arrangement 34 of the coolant pump 11 is formed on the axial side of the coolant pump impeller 20 opposite the inlet 14.
  • This consists of a control pump 36 with a control pump impeller 38, which is integrally formed with the coolant pump impeller 20 and is rotated in accordance with the coolant pump impeller 20.
  • This control pump impeller 38 has blades 40 which are arranged axially opposite to a flow channel 42 designed as a side channel, which is formed in a control pump housing 44.
  • a not visible in this illustration inlet and an outlet 46 are formed, through which the coolant can flow or can flow at elevated pressure.
  • the control pump housing 44 has, just like the housing part 28, an inner axial through opening 48, through which the drive shaft 18 extends with the interposition of a seal 50 in the region of the housing part 28 and is fastened to the housing part 28.
  • a ring-shaped projection 52 facing the housing part 28 is formed on the control pump housing 44, which protrudes into a corresponding receiving opening 49 of the housing part 28, whereby a prefixing takes place.
  • the control pump housing 44 via screws 54, the extend through the control pump housing 44 into corresponding threaded bores of the housing part 28, attached.
  • the movement of the control slide 56 is limited on the one hand by the end of the annular gap 60, on the other hand by the projection 32, against the axial end of a shoulder 64 of the peripheral wall 58 in the completely releasing the annular gap 60 position of the control slide 56 is applied.
  • the control slide 56 has, in addition to the peripheral wall 58, a bottom 66, from the outer periphery of which the circumferential wall 58 extends axially between the control pump housing 44 and the outer housing 10 in the direction of the axially adjoining annular gap 60.
  • a bottom 66 In the radially inner region of the bottom 66 has an opening 68 which is delimited by a hollow cylindrical portion 70, via which the control slide 56 is mounted on the control pump housing 44.
  • a radial groove is formed, in each of which a piston ring 71 is arranged, via which the two axially opposite sides of the control slide 56 are sealed to one another.
  • a first pressure chamber 72 axially through the housing part 28 and the bottom 66 of the control slide 56 and radially outwardly through the outer housing 10 and the annular projection 32 of the housing part 28 and radially inward is limited by the control pump housing 44.
  • a second pressure chamber 74 is formed axially through the bottom 66 and the Rule pump housing 44 is limited radially outward by the peripheral wall 58 of the control slide 56 and radially inwardly by the control pump housing 44.
  • the peripheral wall 58 of the control slide 56 in accordance with the annular gap 60 in or out of the annular gap 60 pushed out.
  • the required pressure difference is generated by the control pump 36, wherein the corresponding pressure in response to the position of a closing member 76 of a 3/2-way solenoid valve 78 to the respective pressure chamber 72, 74 is supplied.
  • a receiving opening 80 for the solenoid valve 78 is formed in the housing part 28, in which a flow housing 82 of the solenoid valve 78 is received.
  • the solenoid valve 78 is shown in FIG. It consists of an electromagnetic actuator 84 and a valve unit 86.
  • the actuator 84 has a winding 90 arranged on a coil support 88, in the interior of which there is a core 92 and which is surrounded axially and radially by flux-conducting elements 94 of the electromagnetic circuit.
  • an axially movable armature 96 is pulled in the direction of the core 92.
  • This movement takes place counter to the force of a spring 98, which is arranged between the core 92 and the armature 96 in a recess 100 on the core 92 and surrounds a non-magnetizable, core 92 fixed pin 102, which serves as a stop for the armature 96, so that it does not abut the core 92 in its shifted position relative to the core 92, since this would lead to undesired adhesive forces.
  • a spring 98 which is arranged between the core 92 and the armature 96 in a recess 100 on the core 92 and surrounds a non-magnetizable, core 92 fixed pin 102, which serves as a stop for the armature 96, so that it does not abut the core 92 in its shifted position relative to the core 92, since this would lead to undesired adhesive forces.
  • the armature 96 mounted in a sliding sleeve 104 mounted in the flow housing 82 has a bore 106 through which the space between the armature 96 and the core 92 is connected to a space on the opposite side of the sliding sleeve 104, thereby preventing that in the interior of the solenoid valve 78 between the armature 96 and the core 92 existing fluid is compressed in the movement of the armature 96 in the direction of the core 92 and thus generates a force counteracting the movement. Instead, the fluid may drain through the bore 106.
  • the valve unit 86 consists of the flow housing 82 and a valve rod 108 fastened to the end of the armature 96, at the end of which the closing element 76 is fastened, which cooperates with two valve seats 110, 112 arranged in the flow housing 82, wherein the valve seat 110 also directly in the housing part 28 can be formed at the end of the receiving opening 80.
  • the closing member 76 has two closing surfaces 114, 116 formed at the opposite axial ends, of which the first closing surface 114 rests on the first valve seat 110 when the actuator 84 is not energized and the other closing surface 116 axially on the second valve seat when the actuator 84 is energized 112 rests.
  • the first valve seat 110 is disposed between a first flow port 118 of the flow housing 82, which is located in the housing part 28, and a second flow port 120
  • the second valve seat 112 is disposed between the second flow port 120 and a third flow port 122, so that either a connection exists between the first two flow ports 118, 120 or exists between the second and third flow ports 120, 122.
  • a first channel 124 in the form of a simple bore is formed in the housing part 28, which leads from the second flow port 120 into the first pressure chamber 72.
  • the first flow connection 118 opens into a second channel 126 formed in the housing part 28, which continues in the control pump housing 44 as far as the outlet 46 of the control pump 36.
  • the annular gap 60 at the outlet 62 of the coolant pump impeller 20 is fully released by the actuator 84 is not energized, whereby the closing member 76 due to the force of the spring 98 with its first closing surface 114th is pressed against the first valve seat 110, whereby the connection of the outlet 46 of the control pump 36 is interrupted to the first pressure chamber 72 and instead a connection of the second flow port 120 and thus of the first pressure chamber 72 to the third flow port 122 is released into a third channel 128th opens, which extends through the housing part 28 radially inward to the passage opening 48.
  • This passage opening 48 extends radially inside the control pump housing 44 through the entire control pump housing 44 to immediately behind theméffenpumpenank 20.
  • This has one or more axial bores 130 through which the coolant to the inlet 14 of the coolant pump 11 can flow, so that the coolant from the first pressure chamber is sucked through the coolant pump 11.
  • the closing of the first valve seat 110 has the consequence that the control pump 36 promotes against the closed first flow port 118. As a result, an increased pressure builds up in the entire flow channel 42, which also acts in the region of the inlet of the control pump 36.
  • a connecting channel 132 is formed in the form of a bore from the flow channel 42 to the second pressure chamber 74, so that this increased pressure builds up in the second pressure chamber 74.
  • This increased pressure in the second pressure chamber 74 has the result that at the bottom 66 of the control slide 56, a pressure difference arises, which causes the control slide 56 is displaced into its annular gap 60 releasing position and thus a maximum delivery of the coolant pump 11 is ensured.
  • An excessive increase in the pressure in the second pressure chamber 74 is avoided inter alia by a leakage between the control pump housing 44 and the peripheral wall 58, so that the additionally funded by the control pump 36 coolant is also used for promotion in the cooling circuit.
  • the solenoid valve 78 is energized again so that the pressure arising at the outlet 46 of the control pump 36 is again transferred to the first pressure chamber 72 is, while the pressure in the second pressure chamber 74 decreases, since in the region of the inlet by the suction of the refrigerant, a reduced pressure.
  • the coolant present in the second pressure chamber 74 is initially aspirated.
  • a pressure difference at the bottom 66 of the control slide 56 is correspondingly again, which causes the control slide 56 is moved into the annular gap 60 and thus the coolant flow in the Cooling circuit is interrupted.
  • a proportional or variable clocked solenoid 78 is used, which also makes it possible to drive the valve 78 in intermediate positions, so that for each position of the control spool 56 when using a proportional valve Force equilibrium can be achieved and according to a complete control of the flow cross-section of the annular gap 60 is made possible.
  • the pressure in the first and second pressure chamber 72, 74 is determined by the time ratio of the open and closed valve. Accordingly, the valve is driven in an oscillating manner via a frequency that is kept low so that the time throughput through the valve can be varied and regulated via the frequency. This allows even more precise control.
  • the described control arrangement is particularly compact by the integration of the solenoid valve and its execution as a 3/2-way valve, however, simple and inexpensive to produce and assemble.
  • On additional lines for hydraulic connection of the control pump with the pressure chambers of the control slide can be omitted, since they can be formed over very short distances as simple holes in the two inner housing parts.
  • the purely hydraulic adjustment of the control slide is very fast with short reaction times.
  • the position required for adjustment in the annular gap closing the control slide Required power reduced by eliminating the return spring, so that a faster adjustment with smaller cross-sections is possible.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Control Of Non-Positive-Displacement Pumps (AREA)
  • Multiple-Way Valves (AREA)
  • Magnetically Actuated Valves (AREA)

Abstract

L'invention concerne des systèmes de régulation de pompes à liquide de refroidissement à régulation mécanique, comportant un tiroir de régulation déplaçable (56) permettant de réguler une section transversale d'écoulement à travers une fente annulaire (60) entre une sortie (62) d'une roue de pompe à liquide de refroidissement (20) et un conduit d'alimentation (12) périphérique, une pompe de régulation (36) permettant de générer une pression hydraulique dans un conduit d'écoulement (42), une première chambre de pression (72) du tiroir de régulation (56) qui est formée sur un premier côté axial du tiroir de régulation (56), une électrovanne (78) munie de deux sièges de vanne (110, 112) et de trois raccordements d'écoulement (118, 120, 122) ainsi que d'un élément de fermeture (76) qui est connecté à un induit (96) de l'électrovanne (78) et mobile axialement, le premier raccordement d'écoulement (118) étant en communication fluidique avec une sortie (46) de la pompe de régulation (36) et le deuxième raccordement d'écoulement (120) étant en communication fluidique avec la première chambre de pression (72) du tiroir de régulation (56). L'invention vise à ce qu'un tel système de régulation puisse être réalisé pour une régulation la plus rapide possible. À cet effet, le troisième raccordement d'écoulement (122) est en communication fluidique avec une entrée (14) de la pompe à liquide de refroidissement (11), le premier siège de vanne (110) étant réalisé entre le premier raccordement d'écoulement (118) et le deuxième raccordement d'écoulement (120), et le second siège de vanne (112) étant réalisé entre le deuxième raccordement d'écoulement (120) et le troisième raccordement d'écoulement (122).
EP16785429.8A 2015-11-06 2016-10-19 Système de régulation d'une pompe à liquide de refroidissement à régulation mécanique d'un moteur à combustion interne Active EP3371463B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102015119098.2A DE102015119098B4 (de) 2015-11-06 2015-11-06 Regelanordnung für eine mechanisch regelbare Kühlmittelpumpe einer Verbrennungskraftmaschine
PCT/EP2016/075072 WO2017076644A1 (fr) 2015-11-06 2016-10-19 Système de régulation d'une pompe à liquide de refroidissement à régulation mécanique d'un moteur à combustion interne

Publications (2)

Publication Number Publication Date
EP3371463A1 true EP3371463A1 (fr) 2018-09-12
EP3371463B1 EP3371463B1 (fr) 2019-11-27

Family

ID=57199978

Family Applications (1)

Application Number Title Priority Date Filing Date
EP16785429.8A Active EP3371463B1 (fr) 2015-11-06 2016-10-19 Système de régulation d'une pompe à liquide de refroidissement à régulation mécanique d'un moteur à combustion interne

Country Status (6)

Country Link
US (1) US11181112B2 (fr)
EP (1) EP3371463B1 (fr)
JP (1) JP6647540B2 (fr)
CN (1) CN108350890B (fr)
DE (1) DE102015119098B4 (fr)
WO (1) WO2017076644A1 (fr)

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JP2014517185A (ja) 2011-04-11 2014-07-17 ノストラム エナジー ピーティーイー．リミテッド 内部冷却式高圧縮リーン・バーン内燃エンジン
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DE102017215984B4 (de) 2017-09-11 2023-11-09 Vitesco Technologies GmbH Steuermodul zur Klimatisierung einer Batterie
WO2020147936A1 (fr) * 2019-01-15 2020-07-23 Pierburg Pump Technology Gmbh Pompe à liquide de refroidissement de véhicule à moteur mécanique commutable
CN112814925B (zh) * 2020-12-31 2022-12-16 蔡长权 一种泵

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DE102011076138A1 (de) * 2011-05-19 2012-11-22 Schaeffler Technologies AG & Co. KG Aktuatorik zur Verstellung einer regelbaren Kühlmittelpumpe
DE102012207387A1 (de) 2011-07-27 2013-01-31 Mahle International Gmbh Kühleinrichtung
DE102013011209B3 (de) 2013-07-04 2014-01-23 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
JP6256142B2 (ja) * 2014-03-26 2018-01-10 株式会社豊田自動織機 遠心圧縮機
DE102014009367B3 (de) 2014-06-21 2015-03-05 Geräte- und Pumpenbau GmbH Dr. Eugen Schmidt Regelbare Kühlmittelpumpe
DE102014110231B3 (de) 2014-07-21 2015-09-10 Nidec Gpm Gmbh Kühlmittelpumpe mit integrierter Regelung
DE102015119097B4 (de) * 2015-11-06 2019-03-21 Pierburg Gmbh Kühlmittelpumpe für eine Verbrennungskraftmaschine

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WO2017076644A1 (fr) 2017-05-11
JP2019500532A (ja) 2019-01-10
DE102015119098A1 (de) 2017-05-11
CN108350890A (zh) 2018-07-31
US11181112B2 (en) 2021-11-23
EP3371463B1 (fr) 2019-11-27
DE102015119098B4 (de) 2019-03-21
US20180320694A1 (en) 2018-11-08
CN108350890B (zh) 2020-02-14
JP6647540B2 (ja) 2020-02-14

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