EP1775478A2 - Pompe de liquide refroidissant - Google Patents

Pompe de liquide refroidissant Download PDF

Info

Publication number
EP1775478A2
EP1775478A2 EP06450133A EP06450133A EP1775478A2 EP 1775478 A2 EP1775478 A2 EP 1775478A2 EP 06450133 A EP06450133 A EP 06450133A EP 06450133 A EP06450133 A EP 06450133A EP 1775478 A2 EP1775478 A2 EP 1775478A2
Authority
EP
European Patent Office
Prior art keywords
pump
coolant
coolant pump
electronics
cooling plate
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.)
Withdrawn
Application number
EP06450133A
Other languages
German (de)
English (en)
Other versions
EP1775478A3 (fr
Inventor
Friedrich Dipl.-Ing. Atschreiter
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.)
TCG Unitech Systemtechnik GmbH
Original Assignee
TCG Unitech Systemtechnik 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 TCG Unitech Systemtechnik GmbH filed Critical TCG Unitech Systemtechnik GmbH
Publication of EP1775478A2 publication Critical patent/EP1775478A2/fr
Publication of EP1775478A3 publication Critical patent/EP1775478A3/fr
Withdrawn legal-status Critical Current

Links

Images

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
    • F04D13/06—Units comprising pumps and their driving means the pump being electrically driven
    • F04D13/0606—Canned motor pumps
    • F04D13/064—Details of the magnetic circuit
    • 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
    • F04D13/0686—Mechanical details of the pump control unit
    • 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
    • F04D29/58—Cooling; Heating; Diminishing heat transfer
    • F04D29/5806—Cooling the drive system
    • 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
    • F04D29/58—Cooling; Heating; Diminishing heat transfer
    • F04D29/5813—Cooling the control unit
    • 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
    • F04D29/58—Cooling; Heating; Diminishing heat transfer
    • F04D29/586—Cooling; Heating; Diminishing heat transfer specially adapted for liquid pumps
    • F04D29/588—Cooling; Heating; Diminishing heat transfer specially adapted for liquid pumps cooling or heating the machine
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2240/00—Components
    • F05D2240/60—Shafts
    • F05D2240/61—Hollow

Definitions

  • the invention relates to a coolant pump, in particular for an internal combustion engine, with a spiral channel in which a pump impeller is arranged, wherein the spiral channel is bounded by a housing cover and a rear wall, with an adjoining the spiral channel electronics chamber for receiving a power electronics and with an adjoining electric motor, which is driven by the power electronics, for driving the pump, wherein the pump impeller is mounted on a drive shaft which is supported by a pump-side bearing and a motor-side bearing, wherein the rear wall of the spiral channel is formed by a cooling plate extending radially over the pump impeller.
  • coolant pump To promote the coolant of the drive motors of motor vehicles increasingly electrically driven coolant pumps are used. Also for a variety of other uses such pumps are used. Usually, the aim is to design the coolant pump as a compact component which, in addition to the drive motor and the actual pump, also contains the power electronics which supply the electric motor. In order to produce the power electronics compact, cost-effective and reliable, it is necessary to ensure efficient cooling. Overall, a simple structure, a versatile applicability and cost manufacturability is required for the pump.
  • a coolant pump is known in which the power electronics is arranged in an electronics chamber which is arranged between the impeller and the electric motor. A secondary flow of the coolant is thereby conveyed from the spiral channel through a connecting channel in a motor chamber, which is located between the electronics chamber and the engine. From this engine chamber, the secondary flow of the coolant passes through the pump-side bearing into a gap between the pump impeller and the electronics chamber, from where it is returned to the spiral channel. Due to the fact that the electronics chamber is adjacent to the motor chamber, the power electronics located in the electronics chamber are cooled.
  • this known solution has proven to be less efficient in practice.
  • the amount of coolant that is conducted in the secondary flow relative limited, since the inflow opening and outflow opening of the bypass system are in spatial proximity, so that the pressure difference, which drives the bypass, is relatively low. Accordingly, the flow rates in the motor chamber are low, which deteriorates the heat transfer.
  • Another disadvantage of the known solution is that the coolant of the secondary flow is heated by the engine, which increases the temperature level and further reduces the cooling effect with respect to the power electronics.
  • the GB 2 330 014 A describes a pump with special cooling channels for cooling of thermally loaded parts of the electric motor.
  • the complex coolant supply requires a complex and error-prone construction. The same applies to a solution as you in the US 5,248,245 A is disclosed.
  • the EP 1 085 217 A2 describes a pump housing with integrated electronics, wherein the pump housing has a receptacle on which the electronic module can be fastened in heat-conducting contact with the pumping medium located in the spiral chamber.
  • the pump housing through which the medium flows and at least partially surrounds the spiral chamber is itself used as a heat sink.
  • sufficient heat dissipation is not guaranteed in all operating situations.
  • Object of the present invention is to develop a coolant pump of the type described above so that the disadvantages described above are avoided and efficient and safe cooling of the power electronics can be guaranteed.
  • a simple and cost-effective design should be achieved.
  • Another object of the invention is to provide a concept that can be easily adapted to different requirements.
  • At least one bypass duct for the coolant is formed between the impeller and the cooling plate, which extends through the pump-side bearing to the electric motor.
  • a large-volume space can be formed by the special design of the cooling plate, which accommodates the power electronics.
  • This electronics chamber is cooled efficiently at its front side by the cooling plate, whereby the cooling effect is considerably improved by a number of synergetic effects over known solutions.
  • the radially outer part of the cooling plate is not acted upon by a secondary flow, but by the main flow of the coolant, wherein a highly turbulent flow with high local flow velocities is present. This ensures highly efficient cooling.
  • forced by the pressure differences in the pump behind the impeller radially inward side stream of the coolant which also has a high cooling effect due to the high flow velocity.
  • the cooling effect is particularly efficient when a bypass duct for the coolant between the impeller and the cooling plate is formed, which extends through the pump-side bearing to the electric motor.
  • the bypass duct continues in a return flow channel which is guided through the hollow drive shaft to the suction side of the pump. In this way it is achieved that the secondary flow of the coolant initially cools the critical power electronics efficiently and is subsequently used for the less critical cooling of the electric motor.
  • a particularly simple construction can be achieved in that the cooling plate carries the pump-side bearing.
  • a positive side effect of this embodiment is also that the secondary flow of the coolant on the radially inner side of the electronics chamber further contributes to the efficient cooling of the power electronics.
  • the cooling plate forms the front side and at least a large part of the radial inner side of the electronics chamber.
  • a particularly advantageous embodiment of the present invention provides that the electronics chamber is limited only by the cooling plate and an electronics cover, which forms the radial outside and the motor-side back of the electronics chamber.
  • the particular advantage of this embodiment is that the basic structure of the pump apart from the electric motor of only three components can be produced, namely the housing cover, the heat sink and the electronics cover.
  • the electronics cover contributes to the isolation of the electronics chamber relative to the electric motor, so that the power density of the power electronics can be further increased.
  • the simplified structure of course ensures cost-effective production.
  • At least one bypass channel flows through or around the electric motor inside and / or outside the stator windings.
  • a particularly good cooling effect can be achieved if at least one inner coolant path of the bypass duct between stator windings and rotor magnet of the electric motor is arranged, wherein preferably at least one outer coolant path of the bypass duct outside the stator windings, preferably between an engine cover and a cover of the electric motor, is arranged.
  • the electronics chamber through the heatsink, an electronics cover forming the motor-side back of the electronics chamber, and a cover cap defining the radial outside of the electronics chamber.
  • the bypass duct extends through a thrust bearing of the drive shaft, which is preferably arranged between the electric motor and the pump-side bearing, wherein the thrust bearing has axial openings for the coolant.
  • the flow through the bypass duct can be increased if the thrust bearing has at least one means for conveying the coolant, wherein preferably the means for conveying the coolant is formed by radial edges or the like on the rotating part of the thrust bearing.
  • the structural design can be simplified in particular in that the cooling plate is clamped between the housing cover and the electronics cover or the cover.
  • a modular concept can be represented with particular advantage in that the pump impeller and the housing cover are designed to be interchangeable for changing the pump performance and characteristic. In this way, pumps of different power and characteristic can be realized with a large number of identical parts.
  • cooling plate is designed as a die-cast aluminum part. It is possible in a particularly efficient manner that the cooling plate has an integrally molded holder and at least one electronic circuit board. It can also be a Hall sensor connection realized in this way easily and inexpensively.
  • the Hall sensors can be integrated in the electronics board (s) and coupled to the heat sink with good thermal conductivity.
  • the required sensor magnets may be disposed on a ring mounted at a suitable location on the rotating shaft.
  • the coolant pump 1 shown in FIGS. 1 to 4 has a pump impeller 2 connected to a drive shaft 3, the drive shaft 3 being driven by an electric motor 4.
  • the stator windings designated by reference numeral 6 with the drive shaft 3 rotor magnets.
  • the drive shaft 3, whose axis of rotation is denoted by 3a, is mounted in the housing 9 via a pump-side bearing 7 and a motor-side bearing 8.
  • the term housing 9 here includes the parts of the housing cover 12, electronics cover 14 and motor cover 15.
  • the bearings 7 and 8 are designed as plain bearings.
  • the pump impeller 2 is arranged in a spiral channel 10 formed by the housing 9.
  • the rear wall of the spiral channel 10 is formed by a cooling plate 11, which extends in the radial direction over the pump impeller 2 and which is sealed off from the spiral cover 10 forming the housing cover 12.
  • the pump-side bearing 7 is supported on the cooling plate 11.
  • Adjacent to the cooling plate 11, an electronics chamber 13 for receiving the power electronics of the electric motor 4 is arranged in the housing 9.
  • the electronics chamber 13 is formed exclusively by the cooling plate 11 and the electronics cover 14, which separates the electronics chamber 13 from the stator windings 5.
  • the electronics cover 14, which may be made of plastic, for example, at the same time forms the housing outer wall of the housing 9.
  • the electric motor 4 is enclosed by the motor cover 15 of the housing 9 of the coolant pump 1, wherein the motor-side bearing 8 is supported on the motor cover 15.
  • At least one bypass duct 16 is provided for coolant between the pump impeller 2 and the cooling plate 11, which extends further through the pump-side bearing 7 to the electric motor 4. Between the stator windings 5 and the rotor magnet 6, the coolant passes to the motor-side bearing 8 and flows through holes in the bearing 8 in a return flow 17 within the drive shaft 3 and further through channels 18 in the hub 19 of the pump impeller 2 on the suction side 20 of the coolant pump 1. The way of the coolant is indicated by the arrows S.
  • the cooling plate 11 is clamped between the electronics cover 14 and the housing cover 12.
  • pump impeller 2 and housing cover 12 can be made interchangeable.
  • the cooling plate 11 may for example consist of die-cast aluminum. On the cooling plate 11, a holder for an electronic board can be formed. Wieters Hall sensors can be integrated into the electronic board and thermally coupled well conductive to the cooling plate 11. Required sensor magnets may be placed on a ring which is mounted at a suitable location on the rotary drive shaft 3 (not shown).
  • FIGS. 5 to 8 show a second embodiment variant of the invention, in which the electronics chamber 13 is formed by an electronics cover 14 and a cover 21, which comprises the motor cover 15.
  • Housing cover 12, electronics cover 14, motor cover 15, as well as the electronics cover 14 and the motor cover 15 enclosing cover are summarized here under the term housing 9.
  • Reference numeral 22 denotes a return ring with an integrated thrust bearing 23.
  • the thrust bearing 23 is arranged between the pump-side bearing 7 and the electric motor 4 and has openings 24 for the coolant flowing through the bypass duct 16.
  • a cavity forms an outer coolant path 25 for the coolant.
  • the outer coolant path 25 may be provided in addition to or in place of the inner coolant path 26 disposed between the stator windings 5 and the rotor magnets 6.
  • the path of the coolant is shown in detail in FIGS. 6 to 8.
  • the coolant flows out of the spiral channel 10 into the bypass channel 16 between the pump impeller 2 and the cooling plate 11. It passes through axial openings 27 in the pump-side bearing 7 to the thrust bearing 23 and flows through axial openings 24 in the thrust bearing 23 on the one hand along the outer coolant path 25 and on the other along the inner coolant path 26 into a return flow channel 17 within the drive shaft 3 and further through bores 18 in the region of the hub 19 onto the pressure side 20 of the coolant pump 1.
  • the thrust bearing 23 supports the conveyance of the coolant through the bypass duct 16.
  • the rotation of the radially outwardly directed part 23a of the thrust bearing 23 produces a conveying effect which enhances the secondary flow due to the pressure difference.
  • the conveying effect can be reinforced by attaching radial ribs - similar to an impeller - or adapted to the requirements.
  • Also by appropriate execution of the apertures 24 can be an amplification of the conveying effect.
  • These openings 24 may be designed as circular holes, or as segments of a circular disk.
  • the radial edges of these apertures 24 may be made oblique to the axis 3a, which also produces a conveying effect. Due to the conveying action of the thrust bearing 23, a large part of the coolant of the bypass duct 16 flows through the outer coolant path 25.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
EP06450133A 2005-10-13 2006-09-21 Pompe de liquide refroidissant Withdrawn EP1775478A3 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
AT0167805A AT502566B1 (de) 2005-10-13 2005-10-13 Kühlmittelpumpe

Publications (2)

Publication Number Publication Date
EP1775478A2 true EP1775478A2 (fr) 2007-04-18
EP1775478A3 EP1775478A3 (fr) 2008-05-21

Family

ID=37216149

Family Applications (1)

Application Number Title Priority Date Filing Date
EP06450133A Withdrawn EP1775478A3 (fr) 2005-10-13 2006-09-21 Pompe de liquide refroidissant

Country Status (2)

Country Link
EP (1) EP1775478A3 (fr)
AT (1) AT502566B1 (fr)

Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2009137323A1 (fr) * 2008-05-06 2009-11-12 Fmc Technologies, Inc. Système de balayage
CN101655095B (zh) * 2009-08-21 2011-12-21 深圳益宝实业有限公司 电动水泵
EP2469093A1 (fr) * 2010-12-24 2012-06-27 Pompes Salmson Pompe de circulation de fluide et son utilisation
WO2012122361A2 (fr) 2011-03-10 2012-09-13 Waters Technologies Corporation Système et procédé de refroidissement d'une tête de pompe utilisée dans une chromatographie
US8696331B2 (en) 2008-05-06 2014-04-15 Fmc Technologies, Inc. Pump with magnetic bearings
EP2609337A4 (fr) * 2010-08-25 2017-12-27 Magna Powertrain Inc. Pompe à eau électrique avec refroidissement de stator
EP3327291A1 (fr) * 2016-11-24 2018-05-30 NIDEC GPM GmbH Pompe électrique à liquide de refroidissement pourvue d'unité de refroidissement ecu
WO2018095607A1 (fr) * 2016-11-25 2018-05-31 Pierburg Pump Technology Gmbh Pompe électrique à liquide de refroidissement pour véhicule automobile
WO2019166118A1 (fr) * 2018-03-02 2019-09-06 Nidec Gpm Gmbh Pompe électrique à réfrigérant
WO2020249396A1 (fr) * 2019-06-11 2020-12-17 HELLA GmbH & Co. KGaA Pompe, en particulier pompe conçue pour un circuit de liquide dans un véhicule
CN113653556A (zh) * 2021-10-21 2021-11-16 威晟汽车科技(宁波)有限公司 一种汽车的电子水泵装置
CN114790996A (zh) * 2022-04-19 2022-07-26 广东美芝制冷设备有限公司 风机和清洁设备
WO2022161791A1 (fr) * 2021-01-29 2022-08-04 HELLA GmbH & Co. KGaA Machine à flux continu radial avec refroidissement et lubrification au moyen d'un milieu qui s'écoule à travers la machine

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009054773A1 (de) * 2009-12-16 2011-06-22 Piller Industrieventilatoren GmbH, 37186 Turboverdichter und Verdichteranlage umfassend einen derartigen Turboverdichter

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1085217A2 (fr) * 1999-09-13 2001-03-21 WILO GmbH Carter de pompe avec électronique intégrée
US20040076532A1 (en) * 2001-01-19 2004-04-22 Yoshiaki Miyazaki Canned motor and canned motor pump
EP1635069A1 (fr) * 2004-09-14 2006-03-15 Dana Automotive Limited Assemblage de pompe

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5248245A (en) * 1992-11-02 1993-09-28 Ingersoll-Dresser Pump Company Magnetically coupled centrifugal pump with improved casting and lubrication
US6012909A (en) * 1997-09-24 2000-01-11 Ingersoll-Dresser Pump Co. Centrifugal pump with an axial-field integral motor cooled by working fluid
DE19916551A1 (de) * 1999-04-13 2000-10-19 Pierburg Ag Kühlmitttelpumpe

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1085217A2 (fr) * 1999-09-13 2001-03-21 WILO GmbH Carter de pompe avec électronique intégrée
US20040076532A1 (en) * 2001-01-19 2004-04-22 Yoshiaki Miyazaki Canned motor and canned motor pump
EP1635069A1 (fr) * 2004-09-14 2006-03-15 Dana Automotive Limited Assemblage de pompe

Cited By (22)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2009137323A1 (fr) * 2008-05-06 2009-11-12 Fmc Technologies, Inc. Système de balayage
US8696331B2 (en) 2008-05-06 2014-04-15 Fmc Technologies, Inc. Pump with magnetic bearings
US8777596B2 (en) 2008-05-06 2014-07-15 Fmc Technologies, Inc. Flushing system
US9601964B2 (en) 2008-05-06 2017-03-21 Fmc Technologies, Inc. In-line flow mixer
CN101655095B (zh) * 2009-08-21 2011-12-21 深圳益宝实业有限公司 电动水泵
EP2609337A4 (fr) * 2010-08-25 2017-12-27 Magna Powertrain Inc. Pompe à eau électrique avec refroidissement de stator
EP2469093A1 (fr) * 2010-12-24 2012-06-27 Pompes Salmson Pompe de circulation de fluide et son utilisation
WO2012122361A2 (fr) 2011-03-10 2012-09-13 Waters Technologies Corporation Système et procédé de refroidissement d'une tête de pompe utilisée dans une chromatographie
EP2683405A4 (fr) * 2011-03-10 2015-12-09 Waters Technologies Corp Système et procédé de refroidissement d'une tête de pompe utilisée dans une chromatographie
US9492764B2 (en) 2011-03-10 2016-11-15 Waters Technologies Corporation System and method of cooling a pump head used in chromatography
EP3327291A1 (fr) * 2016-11-24 2018-05-30 NIDEC GPM GmbH Pompe électrique à liquide de refroidissement pourvue d'unité de refroidissement ecu
WO2018095607A1 (fr) * 2016-11-25 2018-05-31 Pierburg Pump Technology Gmbh Pompe électrique à liquide de refroidissement pour véhicule automobile
US11162511B2 (en) 2016-11-25 2021-11-02 Pierburg Pump Technology Gmbh Electric motor-vehicle coolant pump
WO2019166118A1 (fr) * 2018-03-02 2019-09-06 Nidec Gpm Gmbh Pompe électrique à réfrigérant
CN111801501A (zh) * 2018-03-02 2020-10-20 尼得科Gpm有限公司 电动冷却剂泵
US11708843B2 (en) 2018-03-02 2023-07-25 Nidec Gpm Gmbh Electric coolant pump having a coolant flow path around a stator, a rotor and a control circuit
WO2020249396A1 (fr) * 2019-06-11 2020-12-17 HELLA GmbH & Co. KGaA Pompe, en particulier pompe conçue pour un circuit de liquide dans un véhicule
CN113994100A (zh) * 2019-06-11 2022-01-28 海拉有限双合股份公司 泵、尤其是用于车辆中的液体回路的泵
WO2022161791A1 (fr) * 2021-01-29 2022-08-04 HELLA GmbH & Co. KGaA Machine à flux continu radial avec refroidissement et lubrification au moyen d'un milieu qui s'écoule à travers la machine
CN113653556A (zh) * 2021-10-21 2021-11-16 威晟汽车科技(宁波)有限公司 一种汽车的电子水泵装置
CN114790996A (zh) * 2022-04-19 2022-07-26 广东美芝制冷设备有限公司 风机和清洁设备
CN114790996B (zh) * 2022-04-19 2024-02-06 广东美芝制冷设备有限公司 风机和清洁设备

Also Published As

Publication number Publication date
AT502566B1 (de) 2007-08-15
AT502566A1 (de) 2007-04-15
EP1775478A3 (fr) 2008-05-21

Similar Documents

Publication Publication Date Title
AT502566B1 (de) Kühlmittelpumpe
EP0520333B1 (fr) Unité de pompage
EP2691655B1 (fr) Ventilateur diagonal
EP1716338B1 (fr) Dispositif de transport de fluides
DE102015015863A1 (de) Elektromotorisch angetriebene Flüssigkeitspumpe
EP1778981A1 (fr) Dispositif pour transporter des fluides
DE1613353A1 (de) Ventilator mit einem elektrischen Antriebsmotor
DE3822897A1 (de) Umwaelzpumpe
DE2246265A1 (de) Pumpe mit taumelbarem laeufer
EP3327291B1 (fr) Pompe électrique à liquide de refroidissement pourvue d'unité de refroidissement ecu
EP1387053A1 (fr) Agencement de ventilateur pour refroidir des moteurs de véhicules
WO2020074323A1 (fr) Pompe, en particulier pour un circuit de fluide dans un véhicule
DE102011055599A1 (de) Pumpe für einen Temperaturkreislauf in einem Fahrzeug
EP1945955B1 (fr) Pompe a fluide
EP1794459A1 (fr) Dispositif de circulation de fluides
EP2002123B1 (fr) Pompe a fluide
WO2015067514A1 (fr) Électropompe à eau
DE102018104770A1 (de) Elektrische Kühlmittelpumpe
EP1117169A2 (fr) Refroidissement d'un module électronique par le couvercle du manchon d'entrefer
DE10322464B4 (de) Spaltrohrmotorpumpe
DE102018126775B4 (de) Elektrische Wasserpumpe mit aktiver Kühlung
EP0561864B1 (fr) Ventilateur radial
EP1797330B1 (fr) Dispositif de transport de fluides
EP1945954A1 (fr) Pompe a fluide
DE102004047637B4 (de) Elektrisch betriebene Pumpe mit Außenrotor

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A2

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC NL PL PT RO SE SI SK TR

AX Request for extension of the european patent

Extension state: AL BA HR MK YU

PUAL Search report despatched

Free format text: ORIGINAL CODE: 0009013

AK Designated contracting states

Kind code of ref document: A3

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC NL PL PT RO SE SI SK TR

AX Request for extension of the european patent

Extension state: AL BA HR MK RS

RIC1 Information provided on ipc code assigned before grant

Ipc: F04D 13/06 20060101ALI20080415BHEP

Ipc: F04D 29/58 20060101AFI20061109BHEP

AKX Designation fees paid
REG Reference to a national code

Ref country code: DE

Ref legal event code: 8566

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE APPLICATION IS DEEMED TO BE WITHDRAWN

18D Application deemed to be withdrawn

Effective date: 20081122