EP3006742B1 - Motor vehicle electric coolant pump - Google Patents

Motor vehicle electric coolant pump Download PDF

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Publication number
EP3006742B1
EP3006742B1 EP14188132.6A EP14188132A EP3006742B1 EP 3006742 B1 EP3006742 B1 EP 3006742B1 EP 14188132 A EP14188132 A EP 14188132A EP 3006742 B1 EP3006742 B1 EP 3006742B1
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EP
European Patent Office
Prior art keywords
thrust
thrust washer
motor vehicle
coolant pump
washer arrangement
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.)
Active
Application number
EP14188132.6A
Other languages
German (de)
French (fr)
Other versions
EP3006742A1 (en
Inventor
Wolfgang Zacher
René PATZNER
Gerald PORZ
Alexander Findeisen
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 Pump Technology GmbH
Original Assignee
Pierburg Pump Technology 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 Pump Technology GmbH filed Critical Pierburg Pump Technology GmbH
Priority to EP14188132.6A priority Critical patent/EP3006742B1/en
Publication of EP3006742A1 publication Critical patent/EP3006742A1/en
Application granted granted Critical
Publication of EP3006742B1 publication Critical patent/EP3006742B1/en
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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
    • F04D29/00—Details, component parts, or accessories
    • F04D29/08—Sealings
    • F04D29/16—Sealings between pressure and suction sides
    • F04D29/165—Sealings between pressure and suction sides especially adapted for liquid pumps
    • F04D29/167—Sealings between pressure and suction sides especially adapted for liquid pumps of a centrifugal flow wheel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/04—Shafts or bearings, or assemblies thereof
    • F04D29/041—Axial thrust balancing
    • F04D29/0413—Axial thrust balancing hydrostatic; hydrodynamic thrust bearings
    • 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
    • F04D13/02—Units comprising pumps and their driving means
    • F04D13/06—Units comprising pumps and their driving means the pump being electrically driven
    • F04D13/0606—Canned motor 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
    • F04D29/00—Details, component parts, or accessories
    • F04D29/04—Shafts or bearings, or assemblies thereof
    • F04D29/046—Bearings
    • F04D29/0465—Ceramic bearing designs
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/426—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for liquid pumps
    • F04D29/4273—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for liquid pumps suction eyes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
    • F04D29/669—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for liquid pumps

Definitions

  • the invention relates to an electric motor vehicle coolant pump with a housing that has a pump unit and a motor unit, the pump unit having an inlet and an outlet nozzle, the motor unit having a motor rotor and a motor stator, the motor rotor being an impeller element with vane elements of the pump unit having axially and radially acting bearing means for the motor rotor being provided, a thrust washer arrangement for the impeller member being provided in the inlet connector, the thrust washer arrangement having a thrust member directed towards the impeller member and a damping member facing away from the impeller member.
  • Electric motor vehicle coolant pumps are well known from the prior art. Electric vehicle coolant pumps can be operated exactly as required and consequently adjust the delivery of coolants to the engine temperature. This demand-based delivery means that the motor unit is operated in very different load states, which in turn leads to increased loads on the radial and axial bearings. In particular, the load on the axial bearing can lead to increased noise development in the motor vehicle coolant pump, which is perceived as annoying by the vehicle user or users.
  • An example of such a motor vehicle coolant pump is shown in FIG EP 2 273 123 A1 to find. This document discloses a coolant pump in which a metallic stop ring is provided at the distal end of a rotor axis, which serves as a thrust bearing.
  • a pump according to the preamble of claim 1 is known.
  • the JP 2002 138990 A and the FR 2 911 166 A1 pumps are also known in which a rubber damping element is provided.
  • a pump arrangement is known in which in the area of the rotor and the Inlet stub multi-part axial bearing arrangements are provided, part of the respective axial bearing arrangements being connected to the rotor and part of the axial bearing arrangement being connected to the housing part in the region of the inlet stub. All pump arrangements have in common a complex assembly and a high noise level. The object of the invention is therefore to avoid the above-mentioned disadvantages in a simple and inexpensive manner.
  • the impeller element advantageously has an annular axial shoulder which is in operative connection with the thrust washer arrangement.
  • an inner diameter d 1 of the thrust washer arrangement is advantageously less than or equal to an inner diameter d 2 of a suction mouth of the impeller element. It is also advantageous here if the inner diameter d 1 of the thrust washer arrangement is greater than or equal to an inner diameter d 3 of the inlet connector.
  • FIG. 1 shows an electric motor vehicle coolant pump 2 in a sectional view.
  • the coolant pump 2 has a housing 4 which has a pump unit 6 and a motor unit 8.
  • the housing 4 is designed in several parts for this purpose.
  • the motor vehicle coolant pump 2 is used to pump a liquid cooling fluid, for example water, in a cooling or heating circuit, which can be a main circuit or a secondary circuit, and for this purpose has an axial inlet connector 10 and a tangential outlet connector 12.
  • the pump unit 6 also has an impeller element 14 with blade elements 16, which, driven by the motor unit 8, ensure a cooling fluid delivery from the inlet connector 10 to the outlet connector 12.
  • the impeller member 14 has a suction mouth which is formed here essentially by an annular axial shoulder 18.
  • the impeller element 14 is connected in a known manner to a motor rotor 20 of the motor unit 8
  • Impeller member 14 has a cylindrical extension 22, via which the motor rotor 20, as described further below, is mounted.
  • the motor unit 8 has a motor stator 24 which generates a rotationally moving magnetic field by which the motor rotor 20 is entrained.
  • the motor stator 24 is fluidically separated from the motor rotor 20 by a can 26.
  • the containment shell 26 also forms a bearing mandrel 28 on which the motor rotor 20 is mounted radially via the cylindrical extension 22.
  • a circuit board 30 and a motor plug 32 can be seen in the view, which are used in a known manner for the power supply and the control of the motor vehicle coolant pump 2.
  • a force is exerted on the motor rotor 20 in the direction of the inlet connector 10, as a result of which an axial bearing is to be provided in the area of the end of the motor rotor 20 directed towards the inlet connector 10.
  • This is formed according to the invention by a thrust washer arrangement 34.
  • the thrust washer arrangement 34 consists of a thrust member 36 made of stainless steel which engages in a damping member 38 made of rubber, the damping member 38 being pressed into a recess 40 of the inlet connector 10.
  • the annular axial shoulder 18, which runs onto the stop member 36 in the axial direction, can also be seen here. No axial bearing is to be provided at the end of the motor rotor directed towards the plate 30, since a preferred direction of the motor rotor 20 in the direction of the inlet connector 10 is specified even when there is no delivery.
  • an inner diameter d 1 of the thrust washer assembly 34 less than or equal an inner diameter d 2 of the suction mouth 18 of the impeller body 14.
  • an inner diameter d 1 of the thrust washer assembly 34 greater than or equal an inside diameter d 3 of the inlet connector 10 is selected to be .
  • the invention is only defined by the appended claims and is not restricted to the exemplary embodiment shown here.
  • the motor rotor 20 can also be designed as an external rotor, in which case the radial bearing can also differ significantly from the embodiment shown here.

Description

Die Erfindung betrifft eine elektrische Kfz-Kühlmittelpumpe mit einem Gehäuse, dass eine Pumpeneinheit und eine Motoreinheit aufweist, wobei die Pumpeneinheit einen Einlass- und einen Auslassstutzen aufweist, wobei die Motoreinheit einen Motorrotor sowie einen Motorstator besitzt, wobei der Motorrotor ein Laufradorgan mit Schaufelelementen der Pumpeneinheit aufweist, wobei axial und radial wirkende Lagermittel für den Motorrotor vorgesehen sind, wobei im Einlassstutzen eine Anlaufscheibenanordnung für das Laufradorgan vorgesehen ist, wobei die Anlaufscheibenanordnung ein zum Laufradorgan gerichtetes Anlauforgan und ein vom Laufradorgan abgewandtes Dämpfungsorgan aufweist.The invention relates to an electric motor vehicle coolant pump with a housing that has a pump unit and a motor unit, the pump unit having an inlet and an outlet nozzle, the motor unit having a motor rotor and a motor stator, the motor rotor being an impeller element with vane elements of the pump unit having axially and radially acting bearing means for the motor rotor being provided, a thrust washer arrangement for the impeller member being provided in the inlet connector, the thrust washer arrangement having a thrust member directed towards the impeller member and a damping member facing away from the impeller member.

Derartige elektrische Kfz-Kühlmittelpumpen sind aus dem Stand der Technik hinlänglich bekannt. Elektrische Kfz-Kühlmittelpumpen können exakt bedarfsgerecht betrieben werden und passen folglich die Förderung von Kühlmitteln der Motortemperatur an. Diese bedarfsgerechte Förderung führt dazu, dass die Motoreinheit in ganz unterschiedlichen Lastzuständen betrieben wird, was wiederum zu einer erhöhten Belastung der Radial- und Axiallager führt. Insbesondere die Belastung der Axiallagerung kann hierbei zu einer erhöhten Geräuschentwicklung der Kfz-Kühlmittelpumpe führen, die als störend durch den oder die Fahrzeugnutzer empfunden wird. Ein Beispiel für eine derartige Kfz-Kühlmittelpumpe ist in der EP 2 273 123 A1 zu finden. Diese Druckschrift offenbart eine Kühlmittelpumpe, bei der am distalen Ende einer Rotorachse ein metallischer Anschlagring vorgesehen ist, der als Axiallager dient. Insbesondere aus der JP S64 35098 A ist eine Pumpe gemäß dem Oberbegriff des Anspruchs 1 bekannt. Aus der JP 2002 138990 A und der FR 2 911 166 A1 sind darüberhinaus Pumpen bekannt, bei denen ein Gummidämpfungsorgan vorgesehen ist. Aus der DE 101 04 788 A1 ist eine Pumpenanordnung bekannt, bei der im Bereich des Rotors und des Einlassstutzens mehrteilige Axial-Lageranordnungen vorgesehen sind, wobei ein Teil der jeweiligen Axial-Lageranordnungen mit dem Rotor verbunden ist und ein Teil der Axial-Lageranordnung mit dem Gehäuseteil im Bereich des Einlassstutzens verbunden ist. Allen Pumpenanordnungen ist eine aufwendige Montage und ein hohes Geräuschniveau gemein. Aufgabe der Erfindung ist es daher, die oben genannten Nachteile auf einfache und kostengünstige Weise zu vermeiden.Such electric motor vehicle coolant pumps are well known from the prior art. Electric vehicle coolant pumps can be operated exactly as required and consequently adjust the delivery of coolants to the engine temperature. This demand-based delivery means that the motor unit is operated in very different load states, which in turn leads to increased loads on the radial and axial bearings. In particular, the load on the axial bearing can lead to increased noise development in the motor vehicle coolant pump, which is perceived as annoying by the vehicle user or users. An example of such a motor vehicle coolant pump is shown in FIG EP 2 273 123 A1 to find. This document discloses a coolant pump in which a metallic stop ring is provided at the distal end of a rotor axis, which serves as a thrust bearing. In particular from the JP S64 35098 A a pump according to the preamble of claim 1 is known. From the JP 2002 138990 A and the FR 2 911 166 A1 pumps are also known in which a rubber damping element is provided. From the DE 101 04 788 A1 a pump arrangement is known in which in the area of the rotor and the Inlet stub multi-part axial bearing arrangements are provided, part of the respective axial bearing arrangements being connected to the rotor and part of the axial bearing arrangement being connected to the housing part in the region of the inlet stub. All pump arrangements have in common a complex assembly and a high noise level. The object of the invention is therefore to avoid the above-mentioned disadvantages in a simple and inexpensive manner.

Diese Aufgabe wird durch die Merkmale des Anspruchs 1 gelöst. Hierdurch findet eine Entkopplung der Axialschwingungen des Motorrotors vom Gehäuseteil der Pumpeneinheit statt, was zu einer deutlichen Geräuschreduzierung führt. Auf diese Weise kann die elastische Verbindung zwischen Pumpengehäuse und Anlaufscheibe deutlich gemindert werden, wodurch das Geräuschniveau der Pumpe noch einmal erheblich reduziert wird, da die axialen Bewegungen des Motorrotors gedämpft werden. Die form-, stoff- und/oder kraftschlüssig Anordnung im Einlassstutzen bietet insbesondere hinsichtlich der Montage eine hohe Flexibilität.This object is achieved by the features of claim 1. This decouples the axial vibrations of the motor rotor from the housing part of the pump unit, which leads to a significant reduction in noise. In this way, the elastic connection between the pump housing and the thrust washer can be significantly reduced, as a result of which the noise level of the pump is again considerably reduced, since the axial movements of the motor rotor are dampened. The form-fitting, material-fitting and / or force-fitting arrangement in the inlet connection offers a high degree of flexibility, particularly with regard to assembly.

In vorteilhafter Weise weist das Laufradorgan einen ringförmigen Axialansatz auf, der in Wirkverbindung mit der Anlaufscheibenanordnung steht.The impeller element advantageously has an annular axial shoulder which is in operative connection with the thrust washer arrangement.

Um eine optimale Einströmung des Kühlfluids in die Pumpeneinheit zu gewährleisten, ist in vorteilhafterweise ein Innendurchmesser d1 der Anlaufscheibenanordnung kleiner gleich eines Innendurchmessers d2 eines Saugmundes des Laufradorgans. Hierbei ist es ebenfalls vorteilhaft, wenn der Innendurchmesser d1 der Anlaufscheibenanordnung größer gleich eines Innendurchmessers d3 des Einlassstutzens ist.In order to ensure an optimal inflow of the cooling fluid into the pump unit, an inner diameter d 1 of the thrust washer arrangement is advantageously less than or equal to an inner diameter d 2 of a suction mouth of the impeller element. It is also advantageous here if the inner diameter d 1 of the thrust washer arrangement is greater than or equal to an inner diameter d 3 of the inlet connector.

Die Erfindung wird nachfolgend anhand einer Zeichnung näher erläutert, hierbei zeigt:

  • Figur 1 eine Schnittansicht einer erfindungsgemäßen Kfz-Kühlmittelpumpe, und
  • Figur 2 eine Detailansicht der Anlaufscheibenanordnung aus Figur 1.
The invention is explained in more detail below with reference to a drawing, which shows:
  • Figure 1 a sectional view of a motor vehicle coolant pump according to the invention, and
  • Figure 2 a detailed view of the thrust washer assembly Figure 1 .

Figur 1 zeigt in einer Schnittansicht eine elektrische Kfz-Kühlmittelpumpe 2. Die Kühlmittelpumpe 2 besitzt auf bekannte Weise ein Gehäuse 4, das eine Pumpeneinheit 6 und eine Motoreinheit 8 aufweist. Das Gehäuse 4 ist hierzu mehrteilig ausgebildet. Die Kfz-Kühlmittelpumpe 2 dient zum pumpen eines flüssigen Kühlfluids, beispielsweise Wasser, in einem Kühl- oder Heizkreis, der ein Hauptkreis oder ein Nebenkreis sein kann und weist hierzu einen axialen Einlassstutzen 10 sowie einen tangentialen Auslassstutzen 12 auf. Figure 1 shows an electric motor vehicle coolant pump 2 in a sectional view. In a known manner, the coolant pump 2 has a housing 4 which has a pump unit 6 and a motor unit 8. The housing 4 is designed in several parts for this purpose. The motor vehicle coolant pump 2 is used to pump a liquid cooling fluid, for example water, in a cooling or heating circuit, which can be a main circuit or a secondary circuit, and for this purpose has an axial inlet connector 10 and a tangential outlet connector 12.

Die Pumpeneinheit 6 weist desweiteren ein Laufradorgan 14 mit Schaufelelementen 16 auf, die von der Motoreinheit 8 angetrieben eine Kühlfluidförderung vom Einlassstutzen 10 zum Auslassstutzen 12 gewährleisten. Das Laufradorgan 14 weist in diesem Zusammenhang einen Saugmund auf, der hier im Wesentlichen durch einen ringförmigen Axialansatz 18 ausgebildet ist.The pump unit 6 also has an impeller element 14 with blade elements 16, which, driven by the motor unit 8, ensure a cooling fluid delivery from the inlet connector 10 to the outlet connector 12. In this context, the impeller member 14 has a suction mouth which is formed here essentially by an annular axial shoulder 18.

Das Laufradorgan 14 ist im vorliegenden Ausführungsbeispiel auf bekannte Weise mit einem Motorrotor 20 der Motoreinheit 8 verbunden, wobei das Laufradorgan 14 einen zylinderförmigen Ansatz 22 aufweist, über den der Motorrotor 20, wie weiter unten beschrieben gelagert ist. Desweiteren weist die Motoreinheit 8 einen Motorstator 24 auf, der ein rotatorisch wanderndes Magnetfeld erzeugt, durch den der Motorrotor 20 mitgeschleppt wird. Der Motorstator 24 ist im vorliegenden Ausführungsbeispiel durch einen Spalttopf 26 vom Motorrotor 20 fluidisch getrennt. Der Spalttopf 26 bildet hierbei auch noch einen Lagerdorn 28 aus, auf dem der Motorrotor 20 über den zylinderförmigen Ansatz 22 radial gelagert ist. Desweiteren ist der Ansicht noch eine Platine 30 und ein Motorstecker 32 zu entnehmen, die auf bekannte Weise der Stromversorgung und der Ansteuerung der Kfz-Kühlmittelpumpe 2 dienen. In Förderbetrieb wird auf den Motorrotor 20 eine Kraft in Richtung des Einlassstutzens 10 ausgeübt, wodurch im Bereich des zum Einlassstutzens 10 gerichteten Ende des Motorrotors 20 eine Axiallagerung vorzusehen ist. Diese wird erfindungsgemäß durch eine Anlaufscheibenanordnung 34 ausgebildet.In the present exemplary embodiment, the impeller element 14 is connected in a known manner to a motor rotor 20 of the motor unit 8 Impeller member 14 has a cylindrical extension 22, via which the motor rotor 20, as described further below, is mounted. Furthermore, the motor unit 8 has a motor stator 24 which generates a rotationally moving magnetic field by which the motor rotor 20 is entrained. In the present exemplary embodiment, the motor stator 24 is fluidically separated from the motor rotor 20 by a can 26. The containment shell 26 also forms a bearing mandrel 28 on which the motor rotor 20 is mounted radially via the cylindrical extension 22. Furthermore, a circuit board 30 and a motor plug 32 can be seen in the view, which are used in a known manner for the power supply and the control of the motor vehicle coolant pump 2. In the conveying mode, a force is exerted on the motor rotor 20 in the direction of the inlet connector 10, as a result of which an axial bearing is to be provided in the area of the end of the motor rotor 20 directed towards the inlet connector 10. This is formed according to the invention by a thrust washer arrangement 34.

Wie Figur 2 deutlich zeigt, besteht die Anlaufscheibenanordnung 34 aus einem aus Edelstahl hergestellten Anlauforgan 36, das in ein aus Gummi hergestelltes Dämpfungsorgan 38 eingreift, wobei das Dämpfungsorgan 38 in eine Aussparung 40 des Einlassstutzens 10 eingepresst ist. Zu erkennen ist hier auch der ringförmige Axialansatz 18, der in Axialrichtung auf das Anlauforgan 36 aufläuft. Am zur Platine 30 gerichteten Ende des Motorrotors ist kein Axiallager vorzusehen, da selbst bei Nichtförderung eine Vorzugsrichtung des Motorrotors 20 in Richtung des Einlassstutzens 10 vorgegeben ist.As Figure 2 clearly shows, the thrust washer arrangement 34 consists of a thrust member 36 made of stainless steel which engages in a damping member 38 made of rubber, the damping member 38 being pressed into a recess 40 of the inlet connector 10. The annular axial shoulder 18, which runs onto the stop member 36 in the axial direction, can also be seen here. No axial bearing is to be provided at the end of the motor rotor directed towards the plate 30, since a preferred direction of the motor rotor 20 in the direction of the inlet connector 10 is specified even when there is no delivery.

Um eine optimale Strömungsführung des Kühlfluids zu gewährleisten, ist ein Innendurchmesser d1 der Anlaufscheibenanordnung 34 kleiner gleich eines Innendurchmesser d2 des Saugmundes 18 des Laufradorgans 14. Desweiteren sollte der Innendurchmesser d1 der Anlaufscheibenanordnung 34 größer gleich eines Innendurchmesser d3 des Einlaufstutzens 10 gewählt werden.In order to ensure optimum flow of the cooling fluid is an inner diameter d 1 of the thrust washer assembly 34 less than or equal an inner diameter d 2 of the suction mouth 18 of the impeller body 14. In addition, should the inner diameter d 1 of the thrust washer assembly 34 greater than or equal an inside diameter d 3 of the inlet connector 10 is selected to be .

Desweiteren sollte deutlich sein, dass die Erfindung lediglich durch die beigefügten Ansprüche definiert ist und nicht auf das hier dargestellte Ausführungsbeispiel beschränkt ist. Insbesondere kann der Motorrotor 20 auch als Außenläufer ausgebildet sein, wobei in einem derartigen Fall auch die Radiallagerung deutlich von der hier gezeigten Ausführungsform abweichen kann.Furthermore, it should be clear that the invention is only defined by the appended claims and is not restricted to the exemplary embodiment shown here. In particular, the motor rotor 20 can also be designed as an external rotor, in which case the radial bearing can also differ significantly from the embodiment shown here.

Claims (4)

  1. Electric motor vehicle coolant pump comprising a housing (4) having a pump unit (6) and a motor unit (8), the pump unit (6) having an inlet and an outlet nozzle (10, 12), the motor unit (8) having a motor rotor (20) and a motor stator (24), the motor rotor (20) having an impeller member (14) with blade elements (16) of the pump unit (6), with axially and radially acting bearing means (22, 28; 18, 34) being provided for the motor rotor (20), a thrust washer arrangement (34) for the impeller member (14) being provided in the inlet nozzle (10), the thrust washer arrangement (34) having a thrust element (36) directed towards the impeller element (14) and a damping element facing away from the impeller element (14), the thrust washer arrangement (34) being designed as an axial bearing, the thrust element (36) being made of steel, sintered metal or ceramic, preferably stainless steel, and the damping element (38) being made of rubber, the thrust washer arrangement (24) being arranged in the inlet nozzle (10) in a form-fitting, bonded and/or force-fitting manner, characterized in that the thrust element (36) and the damping element (36) each have a C-shaped radial cross section, such that the thrust element (36) engages in the damping element (38) and the damping element (38) is pressed into the inlet nozzle (10).
  2. Electric motor vehicle coolant pump according to claim 1, characterized in that the impeller member (14) has an annular axial shoulder (18).
  3. Electric motor vehicle coolant pump according to claim 1 or 2, characterized in that an inner diameter d1 of the thrust washer arrangement (34) is smaller than or equal to an inner diameter d2 of a suction nozzle (18) of the impeller member (14).
  4. Electric motor vehicle coolant pump according to one of the preceding claims, characterized in that the inner diameter d1 of the thrust washer arrangement (34) is greater than or equal to an inner diameter d3 of the inlet nozzle (10).
EP14188132.6A 2014-10-08 2014-10-08 Motor vehicle electric coolant pump Active EP3006742B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP14188132.6A EP3006742B1 (en) 2014-10-08 2014-10-08 Motor vehicle electric coolant pump

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP14188132.6A EP3006742B1 (en) 2014-10-08 2014-10-08 Motor vehicle electric coolant pump

Publications (2)

Publication Number Publication Date
EP3006742A1 EP3006742A1 (en) 2016-04-13
EP3006742B1 true EP3006742B1 (en) 2021-12-01

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EP14188132.6A Active EP3006742B1 (en) 2014-10-08 2014-10-08 Motor vehicle electric coolant pump

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Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102017113828A1 (en) * 2017-06-22 2018-12-27 MS-Schramberg Holding GmbH Rotor assembly and method of manufacturing a rotor assembly
DE112020007510T5 (en) 2020-08-20 2023-06-22 Pierburg Pump Technology Gmbh Electronic automotive fluid pump

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AU8739075A (en) * 1974-12-24 1977-06-16 Warman Int Ltd Self centring festrictor bush
JPS6435098A (en) * 1987-07-30 1989-02-06 Ebara Corp Non-volumetric type pump
JP2002138990A (en) * 2000-11-07 2002-05-17 Ebara Corp Motor pump
DE10104788C2 (en) * 2001-02-02 2003-06-26 Federal Mogul Friedberg Gmbh Mechanical seal with radial anti-rotation lock
FR2911166B1 (en) * 2007-01-09 2012-08-03 Siebec Soc PUMP WITH MAGNETIC DRIVE AND SLIDING SEAL
EP2273123B9 (en) 2009-07-08 2018-03-21 Pierburg Pump Technology GmbH Axial bearing for a pump wheel

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

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