EP3455499B1 - Pompe assemblage avec un entraînement mécanique et un entraînement électrique - Google Patents

Pompe assemblage avec un entraînement mécanique et un entraînement électrique Download PDF

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Publication number
EP3455499B1
EP3455499B1 EP17721847.6A EP17721847A EP3455499B1 EP 3455499 B1 EP3455499 B1 EP 3455499B1 EP 17721847 A EP17721847 A EP 17721847A EP 3455499 B1 EP3455499 B1 EP 3455499B1
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EP
European Patent Office
Prior art keywords
impeller
pump group
drive
electric
way coupling
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
EP17721847.6A
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German (de)
English (en)
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EP3455499A1 (fr
Inventor
Alfonso SURACE
Marco Pedersoli
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Industrie Saleri Italo SpA
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Industrie Saleri Italo SpA
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Publication of EP3455499A1 publication Critical patent/EP3455499A1/fr
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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
    • F04D13/00—Pumping installations or systems
    • F04D13/02—Units comprising pumps and their driving means
    • F04D13/021—Units comprising pumps and their driving means containing a coupling
    • 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
    • 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
    • F04D29/049—Roller 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
    • F04D29/00—Details, component parts, or accessories
    • F04D29/18—Rotors
    • F04D29/22—Rotors specially for centrifugal 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
    • F04D29/40—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
    • 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
    • F01P5/02—Pumping cooling-air; Arrangements of cooling-air pumps, e.g. fans or blowers
    • F01P5/04—Pump-driving arrangements
    • F01P2005/046—Pump-driving arrangements with electrical pump drive

Definitions

  • the present invention relates to a pump group for a cooling circuit of a vehicle, preferably for cooling an engine, such as an internal combustion engine.
  • an intense cooling is appropriate when the engine is working at full capacity or in towing conditions or on an uphill road or with high ambient temperatures. In other conditions of use instead, it is appropriate for the cooling not to be accentuated, for example when starting the engine or after use.
  • Cooling pumps are in fact known of for electrically operated vehicles, in which the speed of rotation of the impeller is regulated by means of an electric drive and thus the amount of coolant liquid moved by it in circulation in the cooling circuit.
  • Electrically operated pumps are extremely versatile in their application and in the possibilities of rotation control thanks to the dedicated electronic control, presenting however low delivery power, limited by the electric power provided by the vehicle's electrical system. Furthermore, these pumps do not have the "fail-safe" feature in case of failure, i.e. the possibility to function in an emergency configuration when the electric engine has suffered a breakage.
  • Mechanical pumps are therefore suitable for delivering high power and prove conspicuously reliable but have less versatile cooling control, related to the engine speed and the characteristics of the adjustment element, and are typically too large.
  • no cooling is performed.
  • dual driven pumps are also known of, i.e. comprising both an electric drive and a mechanical drive.
  • Dual-drive pumps are therefore suitable to exploit the advantages of both types of drives, presenting however a particularly complex management of the two drives as well as a particularly articulated structure.
  • An example of a known pump group is disclosed in document DE102014220377A1 .
  • the purpose of the present invention is to provide a pump group for a cooling circuit of a vehicle, for example for an internal combustion engine, which meets the requirements mentioned, over coming the drawbacks spoken of.
  • the purpose of the present invention is to provide a dual drive pump group, with simplified management of the two drives and with a simple and compact structure.
  • FIG. 1 is a schematic cross-section view of a first embodiment of the purrp group of the present invention
  • FIG. 2 shows a schematic cross-section view of a second embodiment of the pump group of the present invention
  • FIG. 3 shows a schematic cross-section view of a third embodiment of the pump group of the present invention.
  • reference numeral 1 globally denotes a pump group for a cooling system of an engine, preferably an internal combustion engine.
  • the pump group 1 of the present invention comprises an impeller 2 rotatable around an axis X-X so that the rotation of the impeller 2 corresponds to the movement of a predetermined quantity of coolant liquid in the circuit.
  • the impeller 2 is of the radial type, i.e. provides that the incoming flow of liquid has an overall substantially axial direction and the flow of liquid in out put has a radial direction.
  • T he impeller 2 comprises a paddle portion 21 provided with a plurality of paddles, which moved in rotation are suitable to performan action on the cool ant liquid.
  • the impeller 2 comprises a support portion 22 which presents a support surface 220 to which a support and centering bearing 20 is operatively connected suitable to support the impeller 2 and keep it centred on the axis X-X, as amply described below.
  • T he pump group 1 provides a dual drive, i.e. operable both mechanically and electrically.
  • the pump group 1 comprises a mechanical drive 3 and an electric drive 5 both operatively connected, as fully described below, to the impeller 2 respectively by means of a first one-way coupling 61 and a second one-way coupling 62.
  • the pump group 1 comprises a mechanical shaft 300 rotatable by the mechanical drive 3 and operatively connected to the impeller 2.
  • the mechanical drive 3 comprises a pulley 33 for a drive belt connected, for example by using a kinematic chain, to the drive shaft.
  • said pulley 33 is of the electromagnetic pulley type so that its activation i.e. its "grip" and its action on the impeller, and its deactivation, i.e. its release, is electrically controllable.
  • the pump group 1 comprises an electric shaft 500 rotatable by the electric drive 5 and, in turn, operatively connected to the impeller 2.
  • the electric drive 5 comprises an electric engine 50 comprising a rotor 51 and a fixed stator 52 coaxial to the rotor 51.
  • said rotor 51 is assembled on a rotor portion 501 of the electric shaft 500; in other embodiments, the rotor 51 is, as described below, directly mounted on a rotation body 8 connected to the impeller 2.
  • the pump unit 1 further comprises an electronic control unit 55 to control the electric drive 5 and/or electromagnetic pulley (if provided).
  • the present invention is not limited to a specific embodiment of the electric drive 5 or its control, as the scope of protection of the invention is solely defined by the appended claims.
  • the drives are both operatively connected with the impeller 2 to control the rotation speed thereof; in the embodiments with the mechanical shaft 300 and electric shaft 500, these are both operatively connected with the impeller 2 to control the rotation speed thereof.
  • the mechanical shaft 300 and electric shaft 500 extend along the axis X-X.
  • the mechanical shaft 300 and the electric shaft 500 extend in two opposite directions, on the two sides of the impeller 2, preferably, in such a way as to present the mechanical drive 3 rearwards of the impeller 2 and the electric drive 5 in front of the impeller 2.
  • the mechanical shaft 300 and the electric shaft 500 extend in the same direction with respect to the impeller 2 one concentric with the other.
  • both the mechanical drive 3 and the electric drive 4 are placed rearwards of the impeller 2; in further embodiments both the mechanical drive 3 and electric drive 4 are placed in front of the impeller 2.
  • the pump group 1 further comprises a rotation body 8 which extends along the axis X-X integrally connected to the impeller 2 to move it in rotation.
  • the electric drive 3 and the mechanical drive 5 are operatively connected to said rotation body 8 by means of the first one-way coupling 61 and the second one-way coupling 62.
  • the electric drive 300 and the mechanical drive 500 are operatively connected to said rotation body 8 to control its rotation by means of the first one-way coupling 61 and the second one-way coupling 62.
  • the rotation body 8 is a rotation shaft. That is to say that the rotation body 8 extends in length along the axis X-X, preferably beyond the height of the impeller 2, for example, extending in front of the paddle portion 21 and/or rearwards of the support portion 22.
  • the rotation body 8 is a central hub. That is to say that the rotation body 8 extends in length along the axis X-X, but substantially by a stretch substantially equal to the height of the impeller 2.
  • the first one-way coupling 61 and the second one-way coupling 62 are co-moulded in the rotation body 8.
  • the rotation body 8 and the impeller 2 are in one piece.
  • the rotation body 8 and the impeller 2 are moulded together.
  • the rotation body 8 has a housing cavity 80 which extends along the axis X-X in which the first one-way coupling 61 and the second one-way coupling 62 are housed.
  • the mechanical shaft impeller end 302 and the electric shaft impeller end 502 are housed in turn inside the rotation body 8.
  • the mechanical shaft impeller end 302 comprises a pin 302' that extends along the axis X-X, while the electric shaft impeller end 502 comprises a housing 502' suitable to house and rotationally support the pin 302'.
  • the electric shaft impeller end 502 comprises a pin which extends along the axis X-X, while the mechanical shaft impeller end 302 comprises a housing suitable to house and rotationally support the pin.
  • said pin is housed in the respective housing comprising a bushing suitable to limit the friction between the two shafts.
  • the pump group 1 comprises a pair of sealing elements 91, 92 operatively connected to the ends of the rotation body 8 to sealingly isolate the housing cavity 80 from the coolant liquid 120.
  • the rotation body 8 has an impeller end 81 to which the impeller 2 is integrally fitted and a drive end 85 to which the first one-way coupling 61 and the second one-way coupling 62 are operatively connected.
  • the impeller end 81 houses internally the first one-way coupling 61 and externally the second one-way coupling 62 (as shown by way of example in Figure 2 ).
  • the drives act through the one-way couplings on the rotation body 8; the latter extending in length presenting a first operating portion 810 on which the first one-way coupling 61 is fitted and a second operating portion 820 on which the second one-way coupling 62 is fitted.
  • these comprise a mechanical shaft impeller end 302 and an electric shaft impeller end 502 operatively connected to the impeller 2 respectively by means of a first one-way coupling 61 and a second one-way coupling 62.
  • the first one-way coupling 61 comprises a rolling bearing for the support in rotation of the electric shaft 300 and/or rotation body 8.
  • the rolling bearing is of the type with rollers or needle rollers, having rolling elements placed between the driven ring and the drive ring.
  • the second one-way coupling 62 comprises a rolling bearing for the support in rotation of the mechanical shaft 500 and/or rotation body 8.
  • the rolling bearing is of the type with rollers or needle rollers, having rolling elements placed between the driven ring and the drive ring.
  • the first one-way coupling 61 and the second one-way coupling 62 are arranged side by side along the axis X-X.
  • the first one-way coupling 61 and the second one-way coupling 62 are arranged with one concentric to the other.
  • the first one-way coupling 61 and the second one-way coupling 62 are axially parallel to the axis X-X, superposed for at least a portion.
  • the support portion 22 of the impeller 2 extends axially along the axis X-X and is positioned rearwards of the paddle portion 21.
  • the support surface 220 is placed in a distal position from the axis X-X, preferably having a circular shape.
  • the support surface 220 has the form of a ring.
  • the support and centering bearing 20 is positioned inside the support surface 220, which is suitable to protect and shelter it.
  • the support and centering bearing 20 is, instead, placed outside the support surface 220.
  • the support and centering bearing 20 is a ball bearing.
  • the support and centering bearing 20 is suitable to support the impeller 2, absorbing the action of the coolant liquid on it, and in particular on the paddle portion 21.
  • the pump group 1 comprises a pump body 10 in which an impeller chamber 120 is defined in which the impeller 2, as well as the rotation body 8, and the support and centering bearing 20 are housed.
  • the coolant liquid is therefore suitable to flow through a suction intake 121, towards an exit mouth 122 in thrust.
  • the impeller chamber 120 is shaped to allow the housing of the impeller 2 and the correct flow of the coolant liquid inside it.
  • the impeller chamber 120 comprises a ring housing 125 in which the support surface 220 and the support and centering bearing 20 are housed.
  • the ring housing 125 is positioned rearwards of the impeller 2 and is specially shaped to allow the housing inside it of the support surface 220 and the support bearing 20.
  • the ring housing 125 has a shape substantially complementary to the space needed to contain the support surface 220 and inside it the support bearing 20.
  • the pair of sealing elements 91, 92 is suitable to sealingly isolate the housing cavity 80 to prevent the coolant liquid 120 in transit in the impeller cavity 120 from wetting the first one-way coupling 61 and the second one-way coupling 62.
  • the pump group 1 is suitable to present all the advantages related to the dual drive.
  • the electromagnetic pulley is activated, in order to disengage the action on the mechanical shaft 300 while the electric drive 5 is left off.
  • the impeller 2 remains stationary, the liquid does not circulate in the circuit and the engine warms up faster.
  • the electric drive 5 is activated in order to place the electric shaft 500 in rotation at a speed greater than that induced by the mechanical drive 3 and by the mechanical shaft 300, thus inducing the impeller 2 to rotate at the speed induced by the electric shaft 500.
  • the first one-way coupling 61 disengages in rotation the impeller 2 from the mechanical shaft 300 reducing the masses dragged in rotation by the electric drive 5.
  • the electric drive 5 is activated so as to keep the impeller 2 rotating (this stage is called "post run").
  • the impeller 2 rotates at a predetermined rotation speed, while the mechanical drive 3 is completely inactive, since the vehicle engine is off.
  • the electromagnetic pulley is not energized, it not being necessary for the movement of the rotation shaft.
  • the first one-way coupling 61 disengages in rotation the impeller 2 from the mechanical shaft 300 reducing the masses dragged in rotation by the electric drive 4.
  • the electric drive 5 is activable whenever it is necessary to increase the cooling capacity, regardless of the mechanical drive 3, related to the engine speed.
  • the quantity of coolant liquid in circulation is regulated by controlling the positioning of further mechanical components placed downstream of the impeller chamber, for example a control valve.
  • the pump group according to the present invention satisfies the cooling requirements of the engine and overcomes the drawbacks referred to above.
  • the pump group according to the invention is very flexible, presenting all the advantages of dual type drives.
  • the pump group is particularly compact and small in dimensions, making it particularly suitable to be housed in the engine compartment of an engine vehicle.
  • a further advantageous aspect lies in the fact that the dual drive of the impeller is controlled by the presence of one-way couplings in a particularly simple and efficient manner, transmitting to the impeller the rotary action induced by the faster drive.
  • the transition from the electric drive to the mechanical drive and vice versa is operated mechanically by the one-way couplings. Therefore, advantageously, the electronic management of the pump group is very simple.
  • the design of the mechanical drive and the electric drive is extremely simplified and is optimisable by the engineer.
  • the electromagnetic pulley if provided, does not require special design updates.
  • the rotor of the electric engine is mounted directly on the electric shaft without the need for special screening bearings, thus limiting the axial dimensions of the rotor.
  • the pump group is able to avoid the cooling action, even though the engine is in gear, when, for example, in conditions of "warm-up", it is appropriate to heat the engine.
  • the pump unit has the "fail safe” characteristic. Indeed, in the event of a failure of the electric drive the pump group, thanks to the mechanical drive and the second one-way coupling, continues to ensure the movement of the impeller.
  • the pump group is operative in "after-run” conditions, i.e. with the engine off.
  • the pump group is operative in "after-run” conditions, i.e. with the engine off.
  • the second one-way coupling in a configuration in which the impeller is made to rotate by the mechanical drive, prevents the rotor from being dragged in rotation by the shaft; magnetic friction is thus not produced (nor does the rotor-stator group work as an electric generator).
  • first one-way coupling and the second one-way coupling are selectable with different characteristics in function of the different actions required of the electric drive and the mechanical drive.
  • a further advantageous aspect lies in the fact that the impeller is supported and kept centred thanks to the presence of the centering and support bearing working directly on it.
  • the one-way couplings are not affected by the action of the coolant liquid, which instead is absorbed by the centering and support bearing.
  • the self-centered and self-supported impeller does not require perfect alignment of the mechanical shaft and electric shaft, when present, nor is it necessary for these to support the rotation body and/or impeller through the couplings.
  • the rotation body and impeller have compact dimensions and are designable to exploit the presence of the centering and support bearing and the advantages it brings.
  • the pump group of the present invention is efficaciously applicable even coupled to next-generation engine groups, typically with engine boosting.
  • engine groups are suitable to deliver high power even at low revs, therefore having a mechanical drive of limited efficiency with consequent limited hydraulic performance of the impeller, recovered by the pump group of the present invention by the electric drive.

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

Claims (13)

  1. Groupe de pompage (1) pour un circuit de refroidissement du moteur d'un véhicule, comprenant :
    - une hélice (2) pouvant être mise en rotation autour d'un axe (X-X), comprenant :
    i) une portion de palette (21) ; et
    ii) une portion de support (22) qui s'étend axialement le long de l'axe (X-X) et est placée derrière la portion de palette (21) ayant une surface de support (220) placée dans une position distale par rapport à l'axe (X-X), ayant de préférence une forme circulaire ;
    - un corps de rotation (8) qui s'étend le long de l'axe (X-X) raccordé solidairement à l'hélice (2) pour la déplacer en rotation, dans lequel le corps de rotation (8) est un arbre de rotation ou moyeu central ;
    - un entraînement mécanique (3) et un entraînement électrique (5) comprenant un moteur électrique (50) ;
    dans lequel l'entraînement mécanique (3) et l'entraînement électrique (5) sont respectivement raccordés fonctionnellement audit corps de rotation (8) par un premier couplage unidirectionnel (61) et un second couplage unidirectionnel (62) ;
    dans lequel le groupe de pompage (1) comprend un palier de support et de centrage (20) positionné sur la surface de support (220) pour supporter et maintenir l'hélice (2) centrée sur l'axe (X-X).
  2. Groupe de pompage (1) selon la revendication 1, dans lequel ledit palier de support et de centrage (20) est positionné à l'intérieur de la surface de support (220).
  3. Groupe de pompage (1) selon l'une quelconque des revendications précédentes, dans lequel le palier de support et de centrage (20) est un roulement à billes.
  4. Groupe de pompage (1) selon l'une quelconque des revendications précédentes, comprenant en outre un corps de pompe (10) dans lequel une chambre d'hélice (120) est identifiée, logeant l'hélice (2) et le palier de support et de centrage (20).
  5. Groupe de pompage (1) selon la revendication 4, dans lequel la chambre d'hélice (120) comprend un logement annulaire (125) dans lequel sont logés la surface de support (220) et le palier de support et de centrage (20).
  6. Groupe de pompage (1) selon l'une quelconque des revendications précédentes, dans lequel le corps de rotation (8) et l'hélice (2) sont d'une seule pièce.
  7. Groupe de pompage (1) selon l'une quelconque des revendications précédentes, dans lequel le corps de rotation (8) possède une cavité de logement (80) le long de l'axe (X-X) dans laquelle sont logés le premier couplage unidirectionnel (61) et le second couplage unidirectionnel (62).
  8. Groupe de pompage (1) selon la revendication 7, comprenant une paire d'éléments d'étanchéité (91, 92) raccordés en fonctionnement aux extrémités du corps de rotation (8) pour isoler de manière étanche la cavité de logement (80) du liquide de refroidissement (120).
  9. Groupe de pompage (1) selon l'une quelconque des revendications 1 à 6 précédentes, dans lequel le corps de rotation (8) possède une extrémité d'hélice (81) sur laquelle est adaptée solidairement l'hélice (2) et une extrémité d'entraînement (85) à laquelle sont raccordés fonctionnellement le premier couplage unidirectionnel (61) et le second couplage unidirectionnel (62).
  10. Groupe de pompage (1) selon l'une quelconque des revendications 1 à 6 précédentes, dans lequel le corps de rotation (8) s'étend en longueur en présentant une première portion fonctionnelle (810) sur laquelle est adapté le premier couplage unidirectionnel (61) et une seconde portion fonctionnelle (820) sur laquelle est adapté le second couplage unidirectionnel (62).
  11. Groupe de pompage selon l'une quelconque des revendications précédentes, comprenant un arbre mécanique (300) pouvant être mis en rotation par l'entraînement mécanique (3) et un arbre électrique (500) pouvant être mis en rotation par l'entraînement électrique (5), dans lequel l'arbre mécanique (300) et l'arbre électrique (500) sont raccordés fonctionnellement au moyen de couplages unidirectionnels respectifs au corps de rotation (8).
  12. Groupe de pompage (1) selon l'une quelconque des revendications précédentes, dans lequel l'entraînement électrique (3) et l'entraînement mécanique (5) s'étendent sur des côtés opposés de l'hélice (2), de préférence de telle sorte que l'entraînement mécanique (3) est placé derrière l'hélice (2) tandis que l'entraînement électrique (5) se trouve devant l'hélice (2).
  13. Groupe de pompage selon l'une quelconque des revendications 1 à 11, dans lequel l'entraînement électrique (5) et l'entraînement mécanique (3) s'étendent du même côté de l'hélice (2) de telle sorte que l'arbre mécanique (300) et l'arbre électrique (500) s'étendent concentriquement l'un par rapport à l'autre.
EP17721847.6A 2016-05-10 2017-03-30 Pompe assemblage avec un entraînement mécanique et un entraînement électrique Active EP3455499B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
ITUA2016A003303A ITUA20163303A1 (it) 2016-05-10 2016-05-10 Gruppo pompa ad azionamento elettrico ed azionamento meccanico con girante supportata
PCT/IB2017/051814 WO2017195049A1 (fr) 2016-05-10 2017-03-30 Groupe de pompes à entraînement électrique et entraînement mécanique, comprenant un rotor supporté

Publications (2)

Publication Number Publication Date
EP3455499A1 EP3455499A1 (fr) 2019-03-20
EP3455499B1 true EP3455499B1 (fr) 2020-07-15

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Application Number Title Priority Date Filing Date
EP17721847.6A Active EP3455499B1 (fr) 2016-05-10 2017-03-30 Pompe assemblage avec un entraînement mécanique et un entraînement électrique

Country Status (5)

Country Link
EP (1) EP3455499B1 (fr)
CN (1) CN109154300B (fr)
HU (1) HUE050224T2 (fr)
IT (1) ITUA20163303A1 (fr)
WO (1) WO2017195049A1 (fr)

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Publication number Priority date Publication date Assignee Title
JP3537349B2 (ja) * 1998-04-20 2004-06-14 日機装株式会社 スラストバランス装置
CN1120937C (zh) * 1998-04-20 2003-09-10 日机装株式会社 推力平衡装置
DE60128631T2 (de) * 2000-09-19 2008-02-07 Aisin Seiki K.K., Kariya Wasserpumpe
GB2404220A (en) * 2003-07-23 2005-01-26 Visteon Global Tech Inc variable speed mechanically-driven vehicular water pump with supplementary electrical drive
DE102006008430A1 (de) * 2006-02-23 2007-08-30 Zf Friedrichshafen Ag Antriebseinrichtung für die Ölpumpe eines Kraftfahrzeuggetriebes
JP4858329B2 (ja) * 2007-06-21 2012-01-18 パナソニック電工株式会社 遠心ポンプ及びこれを備えた液体供給装置
IT1400958B1 (it) * 2010-07-13 2013-07-05 Ind Saleri Italo Spa Pompa di raffreddamento con innesto.
JP2012072701A (ja) * 2010-09-28 2012-04-12 Honda Motor Co Ltd 遠心ポンプ
DE102015216141A1 (de) * 2014-09-03 2016-03-03 Borgwarner Inc. Steuerung für Kühlsystem eines Fahrzeugs
DE102014220377A1 (de) * 2014-10-08 2016-04-14 Mahle International Gmbh Hybrid-Kühlmittelpumpe
CN204663911U (zh) * 2015-05-28 2015-09-23 昆山江津长抗干磨磁力泵有限公司 一种耐腐蚀的离心式磁力潜水泵

Non-Patent Citations (1)

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Title
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Also Published As

Publication number Publication date
EP3455499A1 (fr) 2019-03-20
WO2017195049A1 (fr) 2017-11-16
CN109154300A (zh) 2019-01-04
CN109154300B (zh) 2020-06-09
ITUA20163303A1 (it) 2017-11-10
HUE050224T2 (hu) 2020-11-30

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