EP3676484A1 - Pompe de refroidissement à conception optimisée en fonction de l'application - Google Patents

Pompe de refroidissement à conception optimisée en fonction de l'application

Info

Publication number
EP3676484A1
EP3676484A1 EP18740181.5A EP18740181A EP3676484A1 EP 3676484 A1 EP3676484 A1 EP 3676484A1 EP 18740181 A EP18740181 A EP 18740181A EP 3676484 A1 EP3676484 A1 EP 3676484A1
Authority
EP
European Patent Office
Prior art keywords
pump
shaft
bearing
chamber
coolant
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
EP18740181.5A
Other languages
German (de)
English (en)
Other versions
EP3676484B1 (fr
Inventor
Franz Pawellek
Conrad Nickel
Jens Hoffmann
Robin Büsch
Paul Ludwig
Jakob Schnitzer
Silvio Werner
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 EP3676484A1 publication Critical patent/EP3676484A1/fr
Application granted granted Critical
Publication of EP3676484B1 publication Critical patent/EP3676484B1/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
    • F04D29/00—Details, component parts, or accessories
    • F04D29/08—Sealings
    • F04D29/10—Shaft sealings
    • F04D29/106—Shaft sealings 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
    • F01P5/10—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
    • F04D13/02—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
    • 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
    • F04D13/0633—Details of the 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
    • F04D13/0673—Units comprising pumps and their driving means the pump being electrically driven the motor being of the inside-out 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
    • 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
    • F04D29/00—Details, component parts, or accessories
    • F04D29/04—Shafts or bearings, or assemblies thereof
    • F04D29/046—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
    • F04D29/04—Shafts or bearings, or assemblies thereof
    • F04D29/046—Bearings
    • F04D29/047—Bearings hydrostatic; hydrodynamic
    • F04D29/0473—Bearings hydrostatic; hydrodynamic for radial 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
    • F04D29/06—Lubrication
    • F04D29/061—Lubrication especially adapted for liquid 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
    • F04D29/08—Sealings
    • F04D29/086—Sealings especially adapted for liquid 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
    • F04D29/18—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
    • 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
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P5/00—Pumping cooling-air or liquid coolants
    • F01P5/10—Pumping liquid coolant; Arrangements of coolant pumps
    • F01P5/12—Pump-driving arrangements
    • F01P2005/125—Driving auxiliary pumps electrically
    • 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
    • F01P3/00—Liquid cooling
    • F01P3/20—Cooling circuits not specific to a single part of engine or machine

Definitions

  • the present invention relates to a coolant pump whose structure is optimized by a combination of storage, sealing and electric motor in terms of cost, space and life on the application of a make-up water pump.
  • Such auxiliary electric water pumps are used to circulate portions of a coolant-carrying thermal management system of a vehicle equipped with an internal combustion engine and a main water pump to control so-called hotspots on components such as exhaust gas recirculation, turbocharger, intercooler, or the like such more flexible to cool. Due to the redundancy of the main water pump and the increased number of lines and nodes exist for the type of such additional water pumps a high Preisdruek and high demands on a compact design with small dimensions for integration in a complex packaging modern thermal management systems.
  • wet rotor electric motors of the inner rotor type used in previously established products of electric auxiliary water pumps, i.a. due to the easier seal in the relatively small pump assembly.
  • wet-rotor electric motors in which typically the stator is dry-sealed by a canned or the like relative to the rotor and the rotor and a bearing are designed for operation in the pumped medium, represent a known measure to the problem of a leakage at a Shaft seal and a defect of a shaft bearing counter.
  • wet runners have a lower efficiency, since the gap between the stator and the rotor for receiving a split tube larger fails and a field strength acting on the rotor is thereby weakened.
  • fluid friction occurs on the rotor, which further reduces the efficiency, especially in the relatively small-sized pump drives of additional water pumps.
  • wet-runners experience problems at low temperatures, such as ice formation in the gap between the stator and the rotor.
  • rolling element bearings are generally sensitive to moisture penetration because the materials used, particularly suitable rolling element steels, are not sufficiently corrosion resistant for use in moisture.
  • the ingress of moisture leads by corrosion to the reduction of the surface quality of the rolling elements and raceways, which results in a higher friction of the bearing and corresponding heat development and further consequential damage to bearings and seals.
  • the already costly WälzSh redesignlager in pumps on both ends must be provided with even more costly seals that ensure a low-friction and reliable seal against the working pressures occurring in the pump chamber.
  • Heating systems from the patent application WO 2015/01 1268 AI known which in turn is driven by a wet rotor electric motor.
  • the pump shaft is supported by a radial slide bearing and an axial bearing arranged behind it with a shaft seal.
  • the slide bearing is lubricated by a supply within the pump shaft with the fluid.
  • An axially adjacent rotor space is separated by a membrane with a static sealing function to a receiving space of the stator.
  • a looping of the membrane is called, which leads to a liquid entry into the electrical section of the receiving space, and is to be avoided by a filter in the supply of lubrication.
  • Another aspect of the invention is to provide a pump assembly in which a leakage space between a shaft seal and the dry-rotor electric motor can be omitted in favor of a shorter axial construction of the pump.
  • Another aspect of the invention is to provide a low cost and long lasting alternative to the bearing and sealing of a shaft.
  • the electric coolant pump is characterized in particular by the fact that a radial bearing of the shaft is provided by means of a cooling medium-lubricated radial sliding bearing arranged between the pump impeller and a rotor of a dry-running electric motor; the electric motor is accommodated with a radially inner stator and a radially outer rotor in a motor chamber separated from the pump chamber; a shaft seal is disposed between the radial sliding bearing and the motor chamber; the rotor is formed in a bell shape, the inner surface facing the shaft seal and is fixed axially overlapping with this on the shaft; and the motor chamber an opening to the Atmosphere, which is closed by a liquid-tight and vapor-permeable pressure equalization membrane.
  • the invention in its most general form, the finding is based on the fact that the inventive selection, combination and arrangement of the individual components of the pump, a complementary chain of action from a pressure reduction to limit leakage to a shaft seal, an optimal evaporation of leakage and discharge a vaporized leakage is achieved by taking advantage of operating conditions in the pump, which also provides the tasks corresponding advantages of a constructive and economic nature.
  • the invention provides for the first time for a Troekeneditr electric motor to create a pressure-reduced area for a shaft seal in front of a pumped medium, which is formed axially behind a lubricated by the fluid medium slide bearing.
  • a leakage that occurs at the shaft seal passes, lower.
  • the invention provides for the first time, behind the shaft seal a
  • External rotor type trochanter electric motor with a rotor bell to use whose, preferably closed, inner surface of the shaft seal faces.
  • liquid droplets of leakage past the shaft seal are forced through the air gap of the dry rotor between the open field coils of the stator and the magnetic poles of the rotor by radial acceleration on the inner surface of the rotor bell before they can pass into a motor chamber with electronics.
  • the leakage drops are vaporized by the operating temperature of the electric motor and by a turbulent turbulence in the air gap. The resulting water vapor then enters the motor chamber and escapes through a membrane into the atmosphere.
  • a compact pump construction with a small axial dimension is achieved in which, despite the omission of a leakage space, a permanently safe operating environment for a dry runner in the pump housing is provided.
  • an axial bearing of the shaft can be provided by an axial sliding bearing, which is arranged in a flow direction of the coolant in front of the pump impeller.
  • the axial sliding bearing can be formed by a free end of the shaft and a contact surface on the pump housing, preferably on a pump cover.
  • the pump impeller During operation, the pump impeller generates a thrust force in the direction of the suction port or inlet of the pump.
  • a front-side sliding surface of the shaft and a corresponding housing-side contact surface By a front-side sliding surface of the shaft and a corresponding housing-side contact surface, a particularly simple but sufficient thrust bearing is provided without necessary axial fixation in the opposite direction. Thereby, the structure and the assembly can be further simplified.
  • the shaft seal can have at least two sealing lips for dynamic sealing on the shaft circumference, which are aligned in a sealing manner at least on one axial side.
  • a double-lip shaft seal provides a favorable and sufficient leakage protection behind the axial plain bearing, which achieves a significantly better sealing compared to glazing joints and allows only a small accumulation of leakage drops to pass.
  • a seal in the opposite direction, as in a pump assembly with a dry rolling bearing, can be omitted due to the wet-running plain bearing.
  • the pump housing may include at least one lubrication channel connecting the pump chamber to a rear end of the radial journal bearing opposite the pump chamber.
  • connections from the front and the rear axial end of the sliding bearing to the pumping chamber for lubrication of the sliding bearing can be provided not only a one-sided static loading with funding to the saturation of the bearing gap, but a continuous circulation of funding in the bearing gap. This results in a more even pressure distribution of the Fördenffenn in the bearing gap and a removal of particles by abrasion of the
  • At least one filter may be associated with the at least one lubrication channel.
  • the stator of the electric motor may be arranged in axial overlap with the at least one lubrication channel.
  • Fig. 1 As the axial sectional views in Fig. 1 it can be seen, comprises a pump housing 1 on a left side shown an intake manifold 16 and a discharge nozzle 17, which open into a pump chamber 10.
  • the intake manifold 16 serves as a pump inlet, which is placed in the form of a separate Pumpcndeekels 1 1 on an open axial end of the pump housing 10 and leads to an end face of a pump impeller 2, which is fixed on a shaft 4.
  • the circumference of the pump chamber 10 is surrounded by a spiral housing, which passes tangentially into a pressure port 17, which forms a pump outlet.
  • the impeller 2 is a known Radialpumpenulatelrad with one of the
  • the pump housing 1 On a side shown on the right, the pump housing 1 comprises a designated motor chamber 13 cavity which is separated by a partition 12 of the pump housing 1 of the pump chamber 10, and in which a brushless electric motor 3 is taken from the outer rotor type.
  • a stator 31 with field coils of the electric motor 3 is fixed in the motor chamber 13 around a cylindrical portion of the partition 12 of the pump housing 1.
  • a rotor 32 with permanent-magnetic rotor poles is fixed on the shaft 4 rotatably about the stator 31.
  • An axially open end of the motor chamber 13 is closed by a motor cover of the pump housing 1, in which a control unit or ECU of the pump including a Lcistungselektronik the electric motor 3 is embedded open to the motor chamber 13.
  • a cable feedthrough is arranged on an underside of the pump housing 1, which leads the leads to the field coils on the rotor 32 over.
  • the electric motor 3 is a dry-running type, the field coils of which are unencapsulated or open at the air gap to the rotor 32 to the motor chamber 13.
  • the rotor 32 has a typical for an external rotor bell shape, which sits on the free end of the shaft 4 shown on the right and carries the permanent magnetic rotor poles in the axial region of the stator 31.
  • the rotor 32 does not include apertures in a radially extending portion, as is conventionally conventional for reducing the accelerated mass of rotating support bodies.
  • the bell-shaped rotor 32 preferably forms a closed inner side, which is open only on the left side for receiving the stator 31.
  • the shaft 4 which extends between the pump chamber 10 and the motor chamber 13, is radially supported by a radial sliding bearing 41 in the cylindrical portion of the boundary 12 of the pump housing 1.
  • the sliding surfaces on the shaft periphery and on the bearing seat of the sliding bearing 41 are lubricated by the coolant supplied from the auxiliary water pump, which penetrates into the bearing gap between the sliding surfaces, as will be described later.
  • the shaft 4 is axially supported at the left free end.
  • the axial slide bearing 42 comes about by a pair of sliding surfaces between the end face of the shaft 4 and a contact surface, which is provided by a projection or a strut in the intake manifold 16 in front of the pump impeller 2 appropriately positioned on the pump cover 1 1.
  • the pump impeller 2 pushes the shaft 4 by a suction in the direction of the intake manifold 16 against the contact surface, so that an axial load bearing of the shaft bearing in this one direction is sufficient. Since a bearing gap between the sliding surfaces is surrounded by the flow, and the axial sliding bearing 42 is lubricated with coolant, at least in the form of an initial and re-wetting of the sliding surfaces by the coolant under vibration or turbulence.
  • a shaft seal 5 is arranged, which seals an open end of the cylindrical portion of the partition 12 of the pump housing 1 to the shaft 4.
  • the shaft seal 5 is a double lip seal, which in the cylindrical portion of the partition 12th is pressed, and two successive, directed towards the radial sliding bearing 41 sealing lips (not shown) for unilateral dynamic sealing on the shaft circumference.
  • the coolant contains a antifreeze additive having a friction reducing property, such as e.g. a glycol, silicate or the like. At the same time particles are removed from an abrasion of Gleit vomclamung to the pump chamber and in the flow.
  • a antifreeze additive having a friction reducing property such as e.g. a glycol, silicate or the like.
  • filters 15 are arranged to prevent particulate impurities such as metallic abrasion or the like, to be flushed from the flow in the bearing gap of the radial slide bearing 41 or in the sealing gap of the shaft seal 5.
  • a reduced pressure acts in the annular cavity between the radial slide bearing 41 and the shaft seal 5 due to a flow resistance of the filters 15 compared to the pump chamber 10.
  • the leakage drops vaporize in the air gap between the stator 31 and the rotor 32, without on the radially inner stator 32, a wetting in the liquid phase, ie to be able to exert a corrosive action.
  • the leakage drops can not pass in the axial direction in the engine compartment 13 and the electronics, but are collected on the inner surface of the rotor 32 and fed to the evaporation of the air gap.
  • this is complementary to the circumference of the cylindrical portion of the boundary 12 and the stator 32 is formed stepwise complementary.
  • a diaphragm 6 is provided between the motor chamber 13 and the surrounding atmosphere, which allows a compensation of pressure fluctuations from the motor chamber 13 to the atmosphere.
  • the membrane 6 is semipermeable with respect to water permeability, ie it does not pass water in the liquid phase, whereas moisture-laden air diffuses to a limit with respect to a droplet size or a droplet density that is agglomerated at the membrane surface can.
  • a warm air laden with moisture pass through the membrane 6, so that vaporized leakage drops are effectively discharged into the atmosphere.
  • the membrane 6 in turn protects against the ingress of spray water or the like during driving of the vehicle.
  • the diaphragm 6 closes an opening of the pump housing 1, which is arranged in a region of an outlet of the air gap between the stator 31 and the rotor 32 above.
  • a plug for external power supply is further arranged at the top of the pump housing 1, which is arranged in a region of an outlet of the air gap between the stator 31 and the rotor 32 above.
  • the invention can also be implemented by alternative embodiments with additional features or waiving described features.
  • the pump can also be realized without lubrication channels 14 and filter 15, or with a different axial bearing than the sliding bearing 42 in the region of the intake manifold 16, or with a different shaft seal 5 than that with two sealing lips ,
  • at least one adjustable over the bearing gap static lubrication of the bearing gap of the radial slide bearing 41 can be used by the operating pressure from the pump chamber 10, wherein behind the radial slide bearing 41 again a reduced pressure in comparison to the pump chamber 10 acts on the shaft seal 5.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

L'invention concerne une pompe électrique de refroidissement, de préférence destinée à être utilisée comme pompe à eau auxiliaire dans un véhicule, caractérisée en ce qu'un palier radial de l'arbre (4) est fourni au moyen d'un palier lisse radial (41) lubrifié par un fluide de refroidissement disposé entre la roue de pompe (2) et le rotor (32) ; un moteur électrique (3) fonctionnant à sec ayant un stator (31) radialement intérieur et un rotor (32) radialement extérieur est reçu dans une chambre de moteur (13) séparée de la chambre de pompe (10). Un joint d'étanchéité d'arbre (5) est disposé entre le palier lisse radial (41) et la chambre de moteur (13) ; le rotor (32) a la forme d'une cloche, dont la surface intérieure fait face au joint d'étanchéité d'arbre (5) et est fixée sur l'arbre (4) d'une manière qui se chevauche de façon axiale, et la chambre de moteur (13) présente une ouverture vers l'atmosphère, laquelle ouverture est fermée par une membrane de compensation de pression (6) étanche au liquide et perméable à la vapeur.
EP18740181.5A 2017-08-31 2018-07-10 Pompe de refroidissement optimisé selon l'utilisation Active EP3676484B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102017120039.8A DE102017120039B4 (de) 2017-08-31 2017-08-31 Kühlmittelpumpe mit anwendungsoptimiertem Aufbau
PCT/EP2018/068616 WO2019042638A1 (fr) 2017-08-31 2018-07-10 Pompe de refroidissement à conception optimisée en fonction de l'application

Publications (2)

Publication Number Publication Date
EP3676484A1 true EP3676484A1 (fr) 2020-07-08
EP3676484B1 EP3676484B1 (fr) 2023-08-16

Family

ID=62904460

Family Applications (1)

Application Number Title Priority Date Filing Date
EP18740181.5A Active EP3676484B1 (fr) 2017-08-31 2018-07-10 Pompe de refroidissement optimisé selon l'utilisation

Country Status (6)

Country Link
US (1) US11125244B2 (fr)
EP (1) EP3676484B1 (fr)
CN (1) CN111033008B (fr)
BR (1) BR112020002880A2 (fr)
DE (1) DE102017120039B4 (fr)
WO (1) WO2019042638A1 (fr)

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CN113958497A (zh) * 2020-07-21 2022-01-21 博利源科技(南京)有限公司 无轴封磁力驱动泵浦的前盖结构
LU102208B1 (de) * 2020-11-13 2022-05-17 Wilo Se Selbstentlüftende Nassläuferpumpe
DE102021106969B4 (de) * 2021-03-22 2023-03-16 Audi Aktiengesellschaft Kühlmodul für ein Kraftfahrzeug zum Kühlen einer Antriebseinheit des Kraftfahrzeugs, sowie Kraftfahrzeug und Verfahren zum Montieren eines Kraftfahrzeugs
CN113691071B (zh) * 2021-08-30 2025-05-30 鑫磊压缩机股份有限公司 一种用于防止电机内部腐蚀的固液分离雾化器
FR3145784A1 (fr) 2023-02-15 2024-08-16 Psa Automobiles Sa Pompe hydraulique a ventilation interne
CN116292410B (zh) * 2023-03-22 2025-08-01 天海航空发动机有限公司 一种主动增压水泵
US12571411B2 (en) * 2023-06-06 2026-03-10 General Electric Company Methods and apparatus to remove liquid from a housing

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DE102017120039B4 (de) 2025-02-20
US11125244B2 (en) 2021-09-21
US20210071679A1 (en) 2021-03-11
BR112020002880A2 (pt) 2020-07-28
DE102017120039A1 (de) 2019-02-28
CN111033008A (zh) 2020-04-17
EP3676484B1 (fr) 2023-08-16
CN111033008B (zh) 2021-12-14
WO2019042638A1 (fr) 2019-03-07

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