EP2072825A2 - Pompe à réfrigérant - Google Patents

Pompe à réfrigérant Download PDF

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Publication number
EP2072825A2
EP2072825A2 EP08172030A EP08172030A EP2072825A2 EP 2072825 A2 EP2072825 A2 EP 2072825A2 EP 08172030 A EP08172030 A EP 08172030A EP 08172030 A EP08172030 A EP 08172030A EP 2072825 A2 EP2072825 A2 EP 2072825A2
Authority
EP
European Patent Office
Prior art keywords
rotor
stator
coolant
coolant pump
pump according
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Withdrawn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
EP08172030A
Other languages
German (de)
English (en)
Other versions
EP2072825A3 (fr
Inventor
Eugen Schmidt
Robby Lipfert
André Spörer
Dirk Schmidt
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
Geraete und Pumpenbau GmbH Dr Eugen Schmidt
INA Drives and Mechatronics GmbH and Co KG
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 Geraete und Pumpenbau GmbH Dr Eugen Schmidt, INA Drives and Mechatronics GmbH and Co KG filed Critical Geraete und Pumpenbau GmbH Dr Eugen Schmidt
Publication of EP2072825A2 publication Critical patent/EP2072825A2/fr
Publication of EP2072825A3 publication Critical patent/EP2072825A3/fr
Withdrawn legal-status Critical Current

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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
    • F04D13/06—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
    • F04D15/00—Control, e.g. regulation, of pumps, pumping installations or systems
    • F04D15/02—Stopping of pumps, or operating valves, on occurrence of unwanted conditions
    • F04D15/0245—Stopping of pumps, or operating valves, on occurrence of unwanted conditions responsive to a condition of the pump
    • F04D15/0254—Stopping of pumps, or operating valves, on occurrence of unwanted conditions responsive to a condition of the pump the condition being speed or load
    • 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

Definitions

  • the present invention relates to a coolant pump for conveying a coolant, in particular for use in the cooling circuit of the internal combustion engine of motor vehicles.
  • Coolant pumps for the cooling circuit of internal combustion engines of motor vehicles have hitherto been mainly driven by a V-belt, which is in drive connection with the output of the internal combustion engine.
  • Such coolant pumps had no independent drive unit, which kept the structure simple, but at the same time brought the disadvantage that the delivery and cooling capacity of the coolant pump was directly dependent on the speed of the engine.
  • the coolant pump had to be generously dimensioned, which regularly resulted in excessive coolant delivery at high speeds. The size of the coolant pump was thus unnecessarily large and the efficiency is poor.
  • the installation position of the coolant pump is prescribed by this drive principle, which constructive restrictions on the overall structure of the engine system arise.
  • Another disadvantage of such V-belt driven coolant pumps is that the coolant is also transported immediately after the cold start of the engine, which is undesirable at this time, since in this way increases the time to reach the optimum operating temperature of the engine.
  • the drive unit is formed by a DC motor.
  • the stator of the drive unit is designed as a claw-pole stator and arranged around the rotor running inside.
  • the stator has a bipolar winding for alternately driving to form a magnetic field with alternating polarity.
  • direct drives are known from the prior art, which have an active unit and a passive unit.
  • the active unit includes one or more electrical windings which are driven by a control unit to generate a traveling magnetic field.
  • a running surface of the active unit is opposite a running surface of the passive unit, which has a magnetic tooth pitch and an iron yoke.
  • the passive unit comprises permanent magnets and an iron yoke, wherein embodiments are also known in which the permanent magnets are displaced into the active unit for generating a permanent excitation.
  • a direct drive usually a precise position determination and a complex control is required.
  • Direct drives are usually used as precision drives Use, since only in such applications, the increased control effort justifies.
  • the object of the present invention is to provide an improved coolant pump which avoids the disadvantages of the non-driven coolant pumps, has a simple and inexpensive construction, has a long service life and allows speed control.
  • Such a coolant pump has in known manner a pump unit with a pump and a pumping chamber with suction port and pressure port.
  • a drive unit is provided, which has an electromotive direct drive, which has an active unit with at least one electrical winding as a stator and a permanent-magnet passive unit as a rotor.
  • the coolant pump according to the invention is further distinguished by the fact that the rotor is arranged inside the pump unit-that is to say in the coolant to be delivered-while the stator lies outside the pump unit.
  • Rotor and stator are cylindrical and arranged concentrically to each other.
  • the air gap formed between rotor and stator runs axially, ie parallel to the axis of rotation, and is flowed through by the coolant.
  • the impeller of the pump unit is fixed to the rotor or formed integrally therewith and aligned axially with the axis of rotation.
  • the rotor extends in a rotor sleeve, which adjoins the pumping chamber, so that the coolant can also flow through the rotor sleeve. In this way it is ensured that the rotor is cooled directly by the coolant and that mediates over the coolant flowing through the air gap, the heat generated mainly in the stator can be dissipated well.
  • the rotor is designed as an external rotor while the stator is arranged in a stator sleeve, which extends concentrically within the rotor sleeve.
  • the sealing of the rotor sleeve relative to the pump unit is thereby particularly easy.
  • the bearing of the rotor designed simply, for example by an axis fixed in the stator sleeve on which the rotor is rotatably mounted.
  • the direct drive used to drive the coolant pump is not subject to high precision requirements, so that the position determination of the rotor (passive unit) can be done by simple means, for example by Hall sensors. Deviating from the usual control of a direct drive, it is even sufficient for this application, if the commutation is done without a sensor.
  • the rotor position identification for the commutation takes place in this case via algorithms which evaluate the voltage induction or inductance change of the coil systems in the primary part (in this case stator) when the position of the magnets changes in the air gap; one then speaks of sensorless commutation. In this case, no sensors are needed to control the commutation.
  • known controls for direct drives with higher precision requirements can be used.
  • the impeller is attached to the pump chamber directed to the front side of the rotor or there integrally formed and axially with the Aligned axis of rotation.
  • This design has the advantage that the diameter of the impeller can be kept small, so that the dynamic friction losses remain small at high speeds.
  • the stator sleeve may be formed as an independent component or be formed integrally with the potting material of the stator. Especially with larger designs and high torques, it may be advantageous to pass the rotor axis through the stator sleeve and to extend into the stator, in order to further fix it there. In this way, larger bending moments can be absorbed by the axis. Furthermore, this ensures that the axis really runs axially to the stator lamination.
  • the rotor bearing e.g., bushing or ball bearing
  • the air gap between rotor and stator
  • the bearing of the rotor can be changed, for example, by completely dispensing with the rotor axis and the storage is carried out by a hydrodynamic bearing, which builds up in the air gap between the rotor and stator with the aid of the coolant flowing there.
  • Profiles on the rotor or the rotor sleeve and / or the stator sleeve can be provided in a manner known per se in order to ensure the stability of the hydrodynamic bearing even at low rotational speeds.
  • circuit board on which the electronic control unit of the coolant pump is arranged, is fastened to the side of the stator sleeve facing away from the coolant. In this way, heat loss can be removed from the coolant.
  • Fig. 1 shows in a simplified sectional view of a coolant pump according to the invention, wherein only the most important components are shown.
  • the pump unit of the coolant pump has an impeller 01 with a plurality of vanes 02.
  • the impeller 01 is arranged in a pumping chamber 03, which has a suction port 04 and a pressure port 06.
  • coolant is sucked via the suction connection 04 into the pumping chamber 03 via connected lines (not shown) and discharged at elevated pressure at the pressure connection 06.
  • the flow rate can be changed via the speed of the impeller, which can be set with a connected control unit (not shown).
  • the rotor poles face the electrical winding of the stator 08 with an axially extending air gap 12 therebetween permitting rotation of the rotor.
  • the rotor 07 is positioned in a housing section shaped as a rotor sleeve 13, wherein the pumped coolant from the pumping chamber 03 can flow unhindered into the rotor sleeve 13 and thus also into the air gap 12 in order to dissipate heat from the components flowed around.
  • stator 08 is located in a stator sleeve 14, which is sealed liquid-tight with respect to the rotor sleeve and the pumping chamber. Coolant can thus not reach the electrical winding of the stator 08, so that no special insulation measures are necessary.
  • the stator 08 is suitably fixed inextricably by molding with plastic in the stator sleeve 14.
  • the stator sleeve 14 may be sprayed around the stator by a single process step, or the stator is molded in a prefabricated sleeve. This eliminates additional fasteners and an exact positioning of the stator with respect to the stator is guaranteed by the manufacturer. Especially when encapsulating the stator to form the stator sleeve can be produced small wall thicknesses, whereby the air gap between the stator 08 and rotor 07 can be kept small.
  • Stator, stator sleeve, rotor and rotor sleeve are designed substantially cylindrical and arranged concentrically to each other.
  • the drawn in the figure symmetry axis 16 is thus in the axis of rotation of the rotor.
  • a rotor axis 17 is provided, which extends through the impeller 01 and is fixed to the end face of the stator sleeve 14. If higher bending moments must be recorded, the rotor axis 17 may extend into the stator 08 and / or extend to a bottom plate 18 in order to be fastened there again.
  • the attachment of the rotor axis 17 in the laminated core of the stator allows the absorption of large forces.
  • a bearing 19 is provided on the rotor axis 17, for example a roller bearing or a plain bearing.
  • the rotor shaft 17 is rotatably connected to the stator sleeve 14 in order to avoid sealing problems at this connection point.
  • a securing element (not shown) may be provided to prevent axial displacement of the rotor and the impeller.
  • the stator 08 preferably directly adjoins the bottom plate 18, which in turn closes a housing 22 of the coolant pump on the bottom side.
  • the stator sleeve 14 is sealed against the coolant and the housing 22 is sealed liquid-tight.
  • the housing 22 forming parts are preferably glued or welded together to achieve a liquid-tight connection without additional sealing means.
  • the electrical winding of the stator is supplied via a connecting line 23.
  • the drive unit is constructed in a conventional manner as an electromagnetic direct drive.
  • the control principles for such direct drives are known in the art, so that can be dispensed with a detailed description.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
EP08172030A 2007-12-21 2008-12-17 Pompe à réfrigérant Withdrawn EP2072825A3 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102007055907A DE102007055907A1 (de) 2007-12-21 2007-12-21 Kühlmittelpumpe

Publications (2)

Publication Number Publication Date
EP2072825A2 true EP2072825A2 (fr) 2009-06-24
EP2072825A3 EP2072825A3 (fr) 2012-03-28

Family

ID=40352247

Family Applications (1)

Application Number Title Priority Date Filing Date
EP08172030A Withdrawn EP2072825A3 (fr) 2007-12-21 2008-12-17 Pompe à réfrigérant

Country Status (2)

Country Link
EP (1) EP2072825A3 (fr)
DE (1) DE102007055907A1 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2011035971A3 (fr) * 2009-09-25 2011-10-13 Robert Bosch Gmbh Pompe à moteur électrique
WO2018029116A1 (fr) * 2016-08-08 2018-02-15 Efficient Energy Gmbh Induit électrique plat comprenant un réducteur de pression pour entrefer de moteur
WO2018029115A1 (fr) * 2016-08-08 2018-02-15 Efficient Energy Gmbh Moteur électrique à rotor-disque avec séparation centrale dans l'entrefer de moteur
EP3379085A1 (fr) * 2017-03-23 2018-09-26 Volkswagen Aktiengesellschaft Rotor externe de pompe encapsulé et équilibré

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009009898A1 (de) * 2009-02-20 2010-08-26 Bayerische Motoren Werke Aktiengesellschaft Kühlmittelpumpe für Fahrzeuge
DE102011079226B4 (de) * 2011-07-15 2014-12-24 Bühler Motor GmbH Flüssigkeitspumpe, insbesondere Wasserpumpe
DE102012209487A1 (de) * 2012-06-05 2013-12-05 Mahle International Gmbh Hydrodynamische Pumpe
DE102015207778A1 (de) * 2015-04-28 2016-11-03 Schaeffler Technologies AG & Co. KG Elektrische Maschine
DE102016122784A1 (de) * 2016-11-25 2018-05-30 Pierburg Pump Technology Gmbh Elektrische KFZ-Kühlmittelpumpe
DE102017127851A1 (de) * 2017-11-24 2019-05-29 Nidec Gpm Gmbh Umwälzpumpe mit Nassläufermotor
DE102018104770A1 (de) * 2018-03-02 2019-09-05 Nidec Gpm Gmbh Elektrische Kühlmittelpumpe

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4411960A1 (de) 1994-04-07 1995-10-12 Pierburg Gmbh Elektronisch kommutierter Elektromotor
DE19646617A1 (de) 1996-11-12 1998-05-14 Pierburg Ag Kühlmittelpumpe mit elektrisch kommutiertem Elektromotor
DE19934382A1 (de) 1999-07-22 2001-02-01 Bosch Gmbh Robert Flüssigkeitspumpe

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3752594B2 (ja) * 2000-04-25 2006-03-08 愛三工業株式会社 磁気結合ポンプ
JP2004346774A (ja) * 2003-05-20 2004-12-09 Aisan Ind Co Ltd 磁気結合ポンプ
TW200608869A (en) * 2004-08-30 2006-03-01 Sunonwealth Electr Mach Ind Co Water pump
TWI301743B (en) * 2004-10-15 2008-10-01 Delta Electronics Inc Water pump
CN100529419C (zh) * 2005-07-22 2009-08-19 富准精密工业(深圳)有限公司 液冷散热系统的小型泵体
DE202005019163U1 (de) * 2005-12-07 2006-04-27 Super Electronics Co., Ltd. Außenrotor-Pumpe mit einem innendurchmesserorientierten ringförmigen Ferromagnet
JP2007205190A (ja) * 2006-01-31 2007-08-16 Aisan Ind Co Ltd 電動ポンプ
JP4872456B2 (ja) * 2006-05-24 2012-02-08 パナソニック電工株式会社 ポンプ及び液体供給装置

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4411960A1 (de) 1994-04-07 1995-10-12 Pierburg Gmbh Elektronisch kommutierter Elektromotor
DE19646617A1 (de) 1996-11-12 1998-05-14 Pierburg Ag Kühlmittelpumpe mit elektrisch kommutiertem Elektromotor
DE19934382A1 (de) 1999-07-22 2001-02-01 Bosch Gmbh Robert Flüssigkeitspumpe

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2011035971A3 (fr) * 2009-09-25 2011-10-13 Robert Bosch Gmbh Pompe à moteur électrique
WO2018029116A1 (fr) * 2016-08-08 2018-02-15 Efficient Energy Gmbh Induit électrique plat comprenant un réducteur de pression pour entrefer de moteur
WO2018029115A1 (fr) * 2016-08-08 2018-02-15 Efficient Energy Gmbh Moteur électrique à rotor-disque avec séparation centrale dans l'entrefer de moteur
GB2567582A (en) * 2016-08-08 2019-04-17 Efficient Energy Gmbh Electric disc rotor with a pressure reducer for the motor gap
GB2567581A (en) * 2016-08-08 2019-04-17 Efficient Energy Gmbh Electric disk motor having media separation in the motor gap
GB2567582B (en) * 2016-08-08 2022-06-01 Efficient Energy Gmbh Electric disc armature comprising a pressure reducer for the motor gap
GB2567581B (en) * 2016-08-08 2022-07-13 Efficient Energy Gmbh Electric disk motor with media separation within the motor gap
EP3379085A1 (fr) * 2017-03-23 2018-09-26 Volkswagen Aktiengesellschaft Rotor externe de pompe encapsulé et équilibré

Also Published As

Publication number Publication date
DE102007055907A1 (de) 2009-06-25
EP2072825A3 (fr) 2012-03-28

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