EP3676484B1 - Pompe de refroidissement optimisé selon l'utilisation - Google Patents

Pompe de refroidissement optimisé selon l'utilisation Download PDF

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Publication number
EP3676484B1
EP3676484B1 EP18740181.5A EP18740181A EP3676484B1 EP 3676484 B1 EP3676484 B1 EP 3676484B1 EP 18740181 A EP18740181 A EP 18740181A EP 3676484 B1 EP3676484 B1 EP 3676484B1
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EP
European Patent Office
Prior art keywords
pump
shaft
chamber
coolant
bearing
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
EP18740181.5A
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German (de)
English (en)
Other versions
EP3676484A1 (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
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Nidec GPM GmbH
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Publication date
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Publication of EP3676484A1 publication Critical patent/EP3676484A1/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
    • 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
    • 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
    • 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
    • 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, the design of which is optimized for the application area of an auxiliary water pump in terms of costs, installation space and service life by a combination of a bearing, seal and electric motor.
  • Such electric auxiliary water pumps are used to circulate sub-areas of a coolant-carrying thermal management system of a vehicle that is equipped with an internal combustion engine and a main water pump, in order to cool so-called hotspots on components of auxiliary devices, such as exhaust gas recirculation, a turbocharger, charge air cooling or the like, more flexibly . Due to the redundancy to the main water pump and the increased number of lines and junctions, there is high price pressure for this type of auxiliary water pump and high demands on a compact design with small dimensions for integration in a complex packaging of modern thermal management systems.
  • wet-running electric motors of the internal rotor type are used, among other things due to the simpler sealing in the relatively small pump structure.
  • the use of wet-running electric motors, on which the stator is typically dry-encapsulated from the rotor by a can or the like and the rotor and bearings are designed for operation in the pumped medium, is a known measure to solve the problem of a leak in a Counter shaft seal and a defect in a shaft bearing.
  • wet rotors have a poorer efficiency, since the gap between the stator and the rotor to accommodate a can is larger and a field strength acting on the rotor is thereby weakened.
  • fluid friction occurs on the rotor, as a result of which the efficiency further decreases, particularly in the case of the relatively small pump drives of auxiliary water pumps.
  • problems with wet rotors occur at low temperatures, such as ice formation in the gap between the stator and the rotor.
  • Dry-running electric motors are also used on larger pumps such as the electric main water pumps due to their better efficiency.
  • rolling element bearings such as ball bearings are mainly used, which absorb both axial and radial loads and achieve low coefficients of friction.
  • rolling element bearings are generally sensitive to the ingress of moisture, since the materials used, in particular suitable steels for rolling elements, are not sufficiently corrosion-resistant for use in moisture.
  • the ingress of moisture leads to a reduction in the surface quality of the rolling elements and raceways due to corrosion, which results in higher friction in the bearing and corresponding heat generation and further consequential damage to the bearings and seals.
  • the rolling element bearings in pumps which are expensive anyway, have to be provided with even more expensive seals on both end faces, which ensure low-friction and reliable sealing against the working pressures occurring in the pump chamber.
  • a circulating pump for heating systems from the patent application is also from a generic application WO 2015/011268 A1 known, which in turn is driven by a wet-running electric motor.
  • the pump shaft is supported by a radial slide bearing and an axial bearing with a shaft seal arranged behind it.
  • the slide bearing is lubricated with the pumped medium through a supply inside the pump shaft.
  • a rotor chamber which follows axially behind it is separated from a receiving chamber of the stator by a membrane with a static sealing function.
  • the disclosure does not address the problem of leakage at the shaft seal. As a critical case, however, a grinding through of the membrane is mentioned, which leads to liquid entering the electrical section of the receiving space, and is to be avoided by a filter in the lubrication supply.
  • the DE 100 12 662 B4 a coolant pump and shows the WO 2015/ 121 052 A1 an electric motor as a motor vehicle auxiliary unit.
  • one object of the invention is to create a simple, inexpensive and compact pump structure for a dry-running electric motor.
  • a further aspect of the invention is to create a pump structure in which a leakage space between a shaft seal and the dry-running electric motor can be omitted in favor of a shorter axial structure of the pump.
  • Another aspect of the invention is to provide an inexpensive and durable alternative to bearing and sealing a shaft.
  • the electric coolant pump is characterized in particular by the fact that the motor chamber has an opening to the atmosphere, which is closed by a liquid-tight and vapor-permeable pressure equalization membrane and an axial bearing of the shaft is provided by an axial plain bearing, which is arranged in a direction of flow of the coolant in front of the pump impeller is.
  • the invention in its most general form is based on the knowledge that through the inventive selection, combination and arrangement of the individual components of the pump, a complementary chain of effects from a pressure reduction to limit a leak at a shaft seal, an optimal evaporation of a leak and a discharge an evaporated leakage, is achieved using operating conditions in the pump, which also provides the advantages of a constructive and economic nature that correspond to the tasks.
  • the invention provides for a dry-running electric motor to create a pressure-reduced area for a shaft seal in front of a pumped medium, which is formed axially behind a plain bearing lubricated by the pumped medium. Due to a lower pressure of the pumped medium compared to a corresponding sealing surface within the pump chamber, there is less leakage that occurs at the shaft seal.
  • the invention provides for the use of a dry-running electric motor of the external rotor type with a rotor bell behind the shaft seal, the preferably closed inner surface of which faces the shaft seal.
  • a dry-running electric motor of the external rotor type with a rotor bell behind the shaft seal, the preferably closed inner surface of which faces the shaft seal.
  • a compact pump design with small axial dimensions is achieved in which a permanently safe operating environment is provided for a dry-running pump in the pump housing, despite the omission of a leakage chamber.
  • the axial plain 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 towards the suction port or inlet of the pump.
  • a particularly simple but sufficient axial bearing is provided without the need for axial fixation in the opposite direction. As a result, the construction and 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 at least on one axial side to provide a seal.
  • a double-lipped shaft seal provides cheap and adequate protection against leakage behind the axial plain bearing, which achieves a significantly better seal than mechanical seals and only allows a small accumulation of leakage drops to pass.
  • a seal in the opposite direction, as in a pump design with a dry roller bearing, can be omitted due to the wet-running plain bearing.
  • the pump housing can have at least one lubrication channel, which connects the pump chamber to a rear end of the radial plain bearing that is opposite the pump chamber.
  • One or more connections from the front and the rear axial end of the plain bearing to the pump chamber can be used to lubricate the plain bearing, not just a one-sided static application of funding until the bearing gap is saturated, but also a continuous circulation of funding in the bearing gap. This achieves a more even pressure distribution of the conveying medium in the bearing gap and a removal of particles due to abrasion of the bearing surfaces in favor of better lubrication and less friction.
  • At least one filter can be assigned to the at least one lubrication channel.
  • a filter in each lubrication channel or a filter for all lubrication channels prevents particulate contaminants from entering the bearing gap or the shaft seal .
  • a suitable pressure drop can be set by the nature and thickness of the filter, which results in a pressure-reduced area compared to the pump chamber, which relieves the shaft seal and still ensures sufficient circulation through the bearing gap.
  • the stator of the electric motor can be arranged in axial overlap with the at least one lubrication channel.
  • a pump housing 1 comprises an intake port 16 and a pressure port 17 on a side shown on the left, which open into a pump chamber 10 .
  • the intake port 16 serves as a pump inlet, which is placed in the form of a separate pump cover 11 on an open axial end of the pump housing 10 and leads to an end face of a pump impeller 2 that is fixed on a shaft 4 .
  • the circumference of the pump chamber 10 is of surrounded by a volute, which merges tangentially into a pressure port 17, which forms a pump outlet.
  • the pump impeller 2 is a known radial pump impeller with a central opening adjacent to the intake port.
  • the delivery flow, which flows against the pump impeller 2 through the intake port 16, is accelerated radially outwards by the internal vanes into the spiral housing of the pump chamber 10 and discharged.
  • the pump housing 1 On a side shown on the right, the pump housing 1 includes a cavity called the motor chamber 13 which is separated from the pump chamber 10 by a partition 12 of the pump housing 1 and in which a brushless electric motor 3 of the external rotor type is housed.
  • a stator 31 having field coils of the electric motor 3 is fixed around a cylindrical portion of the partition 12 of the pump housing 1 in the motor chamber 13 .
  • a rotor 32 with permanent magnet rotor poles is rotatably fixed on the shaft 4 around the stator 31 .
  • An axially open end of the motor chamber 13 is closed off by a motor cover of the pump housing 1 in which a control unit or ECU of the pump including power electronics of the electric motor 3 is embedded open to the motor chamber 13 .
  • a cable bushing is arranged on the underside of the pump housing 1, which guides the supply lines to the field coils past the rotor 32.
  • the electric motor 3 is a dry-running type, the field coils of which are unencapsulated or open at the air gap between the rotor 32 and the motor chamber 13 .
  • the rotor 32 has a bell shape that is typical of an external rotor, 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 preferably does not include apertures in a radially extending portion, as is conventional in the art to reduce the accelerated mass on rotating bodies.
  • the bell-shaped rotor 32 preferably forms a closed inside, which is only open on the left side to accommodate 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 section of the boundary 12 of the pump housing 1.
  • the sliding surfaces on the shaft circumference and on the bearing seat of the sliding bearing 41 are lubricated by the coolant delivered by the additional water pump, which penetrates into the bearing gap between the sliding surfaces, as will be described later.
  • the shaft 4 is mounted axially at the left free end.
  • the axial sliding bearing 42 comes about through a sliding surface pairing between the end face of the shaft 4 and a contact surface, which is provided by a projection or a strut in the intake port 16 in front of the pump impeller 2 and positioned accordingly on the pump cover 11 .
  • the pump impeller 2 pushes the shaft 4 by a suction effect in the direction of the intake port 16 against the contact surface, so that an axial load bearing of the shaft bearing is sufficient in this one direction.
  • the axial plain bearing 42 is also lubricated with coolant, at least in the form of an initial wetting of the sliding surfaces by the coolant, which occurs again under vibration or turbulence.
  • a shaft seal 5 is arranged between the radial slide bearing 41 and the motor chamber 13 and seals an open end of the cylindrical section of the partition 12 of the pump housing 1 to the shaft 4 .
  • the shaft seal 5 is a double-lip seal that is pressed into the cylindrical section of the partition 12 and has two sealing lips (not shown) one behind the other, directed in the direction of the radial plain bearing 41, for one-sided dynamic sealing on the shaft circumference.
  • lubrication channels 14 are also introduced into the pump housing 1, on the one hand on a Back of the pump impeller 2 open into the pump chamber 10 and on the other hand lead to an annular cavity surrounding the shaft 4 between the rear end of the radial plain bearing 41 and the shaft seal 5.
  • coolant flows from the pump chamber 10 through the lubrication channels 14 to the shaft 4 and, delimited by the shaft seal 5, penetrates into the bearing gap between the shaft circumference and the bearing seat of the radial plain bearing 41, so that it flows back in the opposite direction.
  • the axial circulation of the coolant in combination with the rotational movement between the sliding surfaces ensures an even distribution and lubrication of the bearing gap with the coolant.
  • the coolant contains an antifreeze additive with a friction-reducing property, such as a glycol, silicate or the like. At the same time, particles from abrasion of the sliding surface pairing are transported away to the pump chamber and into the flow.
  • filters 15 are arranged in the area of the openings of the lubrication channels 14 to the pump chamber 10, which prevent particulate contaminants, such as metallic abrasion or the like, from being washed out of the delivery flow into the bearing gap of the radial plain bearing 41 or into the sealing gap of the shaft seal 5.
  • a reduced pressure acts in the annular cavity between the radial plain bearing 41 and the shaft seal 5 due to a flow resistance of the filter 15 compared to the pump chamber 10.
  • the reduced pressure, which occurs next to the nature of the filter is also adjusted by the number and flow cross-section of the lubrication channels 14, although this weakens the circulation through the radial slide bearing, it also relieves the shaft seal 5, which results in a longer service life for the sealing lips due to less friction and less leakage.
  • the small, unavoidable leakage that occurs drop by drop from the circulation of the lubrication channels 14 through the shaft seal 5 over time does not come into direct contact with the field coils or the motor electronics in the motor chamber 13 .
  • the leakage droplets reach the inner surface of the rotating rotor 32 behind the shaft seal 5 and are carried radially outwards by the centrifugal force.
  • the leakage droplets evaporate in the air gap between the stator 31 and the rotor 32 without wetting the radially inner stator 32 in the liquid phase, ie a to exert a corrosive effect.
  • the leakage droplets cannot reach the engine compartment 13 and the electronics in the axial direction, but are caught on the inner surface of the rotor 32 and fed to the air gap for evaporation.
  • it is stepped in a complementary manner to the peripheries of the cylindrical portion of the boundary 12 and the stator 32 .
  • the transition of leakage droplets from the liquid to the gaseous phase is accompanied by an increase in volume, which would lead to an increase in pressure in the case of a closed volume of the motor chamber 13, regardless of a pressure fluctuation that would occur due to temperature fluctuations between operation and standstill of the pump.
  • a membrane 6 is provided between the motor chamber 13 and the surrounding atmosphere, which enables pressure fluctuations from the motor chamber 13 to be compensated for with the atmosphere.
  • the membrane 6 is semi-permeable with regard to water permeability, ie it does not allow water to pass through in the liquid phase, whereas air laden with moisture can diffuse through up to a limit with regard to a droplet size or a droplet density agglomerating on the membrane surface.
  • warm air laden with moisture can pass through the membrane 6, so that evaporated leakage droplets are effectively discharged into the atmosphere.
  • the membrane 6 in turn protects against the ingress of spray water or the like when the vehicle is being driven.
  • the membrane 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 the external power supply is also arranged on the upper side of the pump housing 1 .
  • the invention can also be implemented by alternative configurations with additional features or by omitting the features described.
  • the pump can also be implemented without lubrication channels 14 and filter 15, or with an axial bearing other than the slide bearing 42 in the area of the intake port 16, or with a shaft seal 5 other than the one with two sealing lips .
  • at least static lubrication of the bearing gap of the radial plain bearing 41 which can be adjusted via the bearing gap, can be used by the operating pressure from the pump chamber 10, with a reduced pressure behind the radial plain bearing 41 in turn being compared to the pump chamber 10 acts on the shaft seal 5.

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  • 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)

Claims (7)

  1. Pompe à liquide de refroidissement électrique pour le transport d'un liquide de refroidissement dans un véhicule, présentant :
    un carter de pompe (1) avec une chambre de pompe (10), dans laquelle une roue de pompe (2) est reçue de manière rotative, une entrée (16) et une sortie (17), qui sont reliées à la chambre de pompe (10) ;
    un arbre (4), qui est monté rotatif sur le carter de pompe (1), et sur lequel la roue de pompe (2) est fixée ; dans laquelle
    un montage radial de l'arbre (4) est fourni au moyen d'un palier lisse radial (41) lubrifié par un fluide de refroidissement, qui est disposé entre la roue de pompe (2) et le rotor (32) ;
    un moteur électrique (3) fonctionnant à sec avec 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'arbre (5) est disposé entre le palier lisse radial (41) et la chambre de moteur (13) ; et
    le rotor (32) est réalisé sous une forme de cloche, dont la surface intérieure est tournée vers le joint d'arbre (5) et fixée sur l'arbre (4) de manière à chevaucher celui-ci axialement ;
    caractérisée en ce que
    la chambre de moteur (13) présente une ouverture par rapport à l'atmosphère, qui est fermée par une membrane de compensation de pression (6) étanche au liquide et perméable à la vapeur, et
    un montage axial de l'arbre (4) est fourni par un palier lisse axial, qui est disposé devant la roue de pompe (2) dans une direction d'écoulement du liquide de refroidissement.
  2. Pompe à liquide de refroidissement électrique selon la revendication 1, dans laquelle
    le palier lisse axial (42) est formé par une extrémité libre de l'arbre (4) et une surface d'appui sur le carter de pompe (1), de préférence un couvercle de pompe (11).
  3. Pompe à liquide de refroidissement électrique selon la revendication 1 ou 2, dans laquelle
    le joint d'arbre (5) présente au moins deux lèvres d'étanchéité pour l'étanchéification dynamique sur la circonférence de l'arbre, qui sont orientées de manière à avoir une action étanche au moins par rapport à une face axiale.
  4. Pompe à liquide de refroidissement électrique selon l'une quelconque des revendications 1 à 3, dans laquelle
    le carter de pompe (1) présente au moins un canal de lubrification (14), qui relie la chambre de pompe (10) à une extrémité arrière du palier lisse radial (41) opposée à la chambre de pompe (10).
  5. Pompe à liquide de refroidissement électrique selon la revendication 4, dans laquelle
    au moins un filtre (15) est associé au au moins un canal de lubrification (14).
  6. Pompe à liquide de refroidissement électrique selon l'une quelconque des revendications 4 ou 5,
    dans laquelle le stator (31) du moteur électrique (3) est disposé en chevauchement axial avec le au moins un canal de lubrification (14).
  7. Utilisation d'une pompe à liquide de refroidissement électrique selon l'une quelconque des revendications 1 à 6 comme pompe à eau supplémentaire dans un système acheminant un liquide de refroidissement dans un véhicule avec un moteur à combustion interne et une pompe à eau principale.
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 EP3676484A1 (fr) 2020-07-08
EP3676484B1 true EP3676484B1 (fr) 2023-08-16

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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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CN111033008A (zh) 2020-04-17
EP3676484A1 (fr) 2020-07-08
US11125244B2 (en) 2021-09-21
CN111033008B (zh) 2021-12-14
DE102017120039A1 (de) 2019-02-28
US20210071679A1 (en) 2021-03-11
BR112020002880A2 (pt) 2020-07-28
DE102017120039B4 (de) 2025-02-20
WO2019042638A1 (fr) 2019-03-07

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