EP3924624B1 - Pompe à vis à liquide de refroidissement électrique - Google Patents

Pompe à vis à liquide de refroidissement électrique Download PDF

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Publication number
EP3924624B1
EP3924624B1 EP19817281.9A EP19817281A EP3924624B1 EP 3924624 B1 EP3924624 B1 EP 3924624B1 EP 19817281 A EP19817281 A EP 19817281A EP 3924624 B1 EP3924624 B1 EP 3924624B1
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EP
European Patent Office
Prior art keywords
motor
housing
chamber
spindle
electric
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
EP19817281.9A
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German (de)
English (en)
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EP3924624A1 (fr
Inventor
Daniel Döhler
Franz Pawellek
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
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.)
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Publication date
Application filed by Nidec GPM GmbH filed Critical Nidec GPM GmbH
Publication of EP3924624A1 publication Critical patent/EP3924624A1/fr
Application granted granted Critical
Publication of EP3924624B1 publication Critical patent/EP3924624B1/fr
Active 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
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/12—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C2/14—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F04C2/16—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0096—Heating; Cooling
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/04—Heating; Cooling; Heat insulation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/04—Heating; Cooling; Heat insulation
    • F04C29/047—Cooling of electronic devices installed inside the pump housing, e.g. inverters
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/40—Electric motor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/80—Other components
    • F04C2240/808—Electronic circuits (e.g. inverters) installed inside the machine

Definitions

  • the present invention relates to an electric coolant pump of a screw pump type for pumping a coolant circuit or the like, particularly for pumping corrosive liquid media.
  • Screw pumps are positive displacement pumps that allow high pressures and high volumetric efficiency. They do not offer speed-independent adjustment of the geometry, but they have a dirt-resistant, robust rotary piston mechanism that does not require filigree elements such as locking slides or the like. As a result, mechanically driven screw pumps have so far mainly been used in large-scale applications, such as oil pumps in stationary systems or ship engines, in which they run at relatively constant operating points.
  • the DE 10 2015 101 443 B3 describes a fuel pump with a housing in which an electric drive motor is coupled to a screw pump. The fuel flows through the drive motor before leaving the outlet on the pressure side.
  • the WO 2014/138519 A1 discloses a screw type electric fluid pump.
  • the fluid flowing through an inlet and an outlet also surrounds the motor.
  • a fuel is mentioned as a liquid.
  • a flange plane which is drawn in the illustrated construction between a motor-side housing part and a pump-side housing part, runs between the motor and a pump-side outlet.
  • the DE 10 2017 210 771 A1 shows an electrically driven screw pump as a fuel delivery unit.
  • a pump housing and an electric motor are accommodated in a casing.
  • the electrical components of the motor are in direct contact with the fuel within an outlet guide on a pressure side of the spindle chamber.
  • the pumps mentioned above cannot be transferred to an application as an electric water pump, in particular not as an electric coolant pump.
  • a liquid conveying medium such as a coolant would cause corrosive damage to the exposed components of the electric motor, in particular the coil windings of the stator.
  • the US 6,371,744 B1 describes a screw type electric vacuum pump.
  • the screw spindles are driven by an electric motor that is located in a separate housing.
  • the WO2017/059501 A1 describes a screw compressor with an intermediate housing for a gearbox.
  • a setpoint temperature of a coolant may be in the range of the boiling temperature of the coolant. In this case, overheating damage to electrical or electronic components would occur in continuous operation.
  • one object of the present invention is to create an electric screw pump that is suitable for pumping corrosive, liquid media and cooling of the provides electric drive.
  • a further partial aspect of the task consists in providing a corresponding technical solution in such a way that it can also be implemented cost-effectively in series production of large quantities.
  • the electric screw spindle coolant pump according to the invention for conveying a coolant circuit is characterized in particular by the fact that a motor housing comprises a motor chamber in which a dry-running electric motor is arranged, separated from the conveying flow; and that the motor housing has a heat transfer section through which the delivery flow flows, which is arranged between the motor chamber and a component boundary of the motor housing to a spindle housing.
  • the invention provides for the first time a screw pump as a coolant pump.
  • the invention provides for the first time a screw spindle pump as an electric liquid pump which is driven by a dry-running electric motor.
  • the invention provides for the first time a screw spindle pump as an electric liquid pump in which a convection-assisted heat transfer from a dry motor chamber to a delivery flow of the liquid delivery medium is provided.
  • a coolant pump with a high power density is created by the present invention.
  • the screw pump provides the high delivery pressure of a positive displacement pump, but with a relatively low pulsation, similar to that of a centrifugal pump.
  • the screw pump enables universal installations and applications.
  • the electric screw spindle coolant pump according to the invention is suitable, for example, for use in electric, in particular battery-electric vehicles, in which no mechanical drive source is provided and a branched structure of thin or capillary cooling channels in a battery module or a traction motor requires a high delivery pressure.
  • the invention is based on a principle of shifting an axial position of a component boundary between a motor housing and a spindle housing from a conventional functional position further in the direction of the spindle chamber.
  • this creates an area that is protected from the liquid in the delivery flow, so that the electric drive is not exposed to any corrosive influences.
  • the heat transfer section creates a liquid-conducting area on the motor housing, which increases an internal thermal contact area with the coolant. Even with a small temperature difference between the electric drive and the coolant, waste heat from electrical power loss can be effectively removed from the pump via a heat exchange on the resulting thermal contact surface of the heat-conducting motor housing and convection of the flow.
  • the increase in the thermal contact area is achieved without a higher complexity of the structure, such as in the form of surface-enlarging structures, flow resistances or the like.
  • the motor housing is designed as a cast part in product development.
  • the changed component limit can be implemented on the pump structure according to the invention without any significant effort or increase in production costs. Due to a complementary relocation of the component boundary of the spindle housing, there is essentially no disadvantageous increase in the overall dimensions of the pump, despite an increased axial dimension of the motor housing.
  • the heat transfer section may further include the pump outlet.
  • the flow cross-section of the entire flow is guided past the motor chamber.
  • the inner surface of the pump outlet at the heat transfer section increases the thermal contact surface of the thermally conductive motor housing with the delivery flow again considerably.
  • the heat transfer section may include a flow chamber that establishes communication between the end boundary of the motor chamber and the spindle chamber.
  • the heat transfer portion may include a bearing seat for a shaft bearing disposed between the electric motor and the screw rods.
  • the surface of the bearing seat in the heat transfer section in turn increases the thermal contact area of the thermally conductive motor housing with the flow.
  • the integration of a shaft bearing in the axial area of the heat transfer section promotes a compact construction of the pump.
  • electronics for the electric motor can also be arranged in the motor chamber. Accordingly, a further heat source is included in the cooling of the electric drive according to the invention. In this way, the power loss from power electronics is also dissipated via the flow.
  • a stator and/or electronics of the electric motor in the motor housing can be in contact with a front-side delimitation of the motor chamber. This ensures that the heat transfer distance of the thermally conductive motor housing between the electrical heat sources in the motor chamber and the flow is as short as possible.
  • the heat transfer portion may be formed integrally with the motor housing. This ensures an optimized heat transfer path without boundary surfaces or gaps in the material and the lowest possible manufacturing costs for the motor housing.
  • the spindle housing can be designed in one piece. As explained above, the shifting of the component boundary between the motor housing and the spindle housing results in an open cross-section of the spindle chamber. As a result, no division into two halves of the housing is required either for assembly of the pump or for the production of the shaped body of the spindle housing.
  • the one-piece design of the spindle housing ensures a smooth inner contour of the spindle chamber without the need for post-processing.
  • the inner contour of the spindle chamber can be produced simply and precisely by drilling.
  • the spindle housing may include the pump inlet.
  • the spindle housing is designed as a cast part in product development. Consequently, by integrating the pump inlet, the number of components of the pump structure according to the invention can be reduced without significant effort.
  • a flange connection made up of a flange section of the motor housing and a flange section of the spindle housing can be formed at the component boundary between the motor housing and the spindle housing.
  • the flange connection enables a preferred screw connection for assembling the two housing components, while a corresponding flange level allows different types of sealing.
  • screw pump is understood to mean helical geared rotary piston pumps with a thread pitch for displacement of the pumped medium.
  • Such types of pumps usually comprise a driven screw spindle 2a and at least one further screw spindle 2b, which is dragged along by engagement of the gearing.
  • the spindle chamber 10 has a cross-sectional contour in the form of a so-called aft housing, ie it is formed by two bores in the pump housing 1, the radii of which overlap in order to ensure engagement of the screw spindles 2a, 2b.
  • the driven screw spindle 2a is connected to an electric motor 4 .
  • a rotational movement of engaged screw profiles of the rotating screw spindles 2a, 2b generates a negative pressure on the suction side of the spindle chamber 10 and an overpressure on the opposite pressure side of the spindle chamber 10.
  • the conveyed medium is conveyed by a continuous displacement along a screw pitch of the engaged screw profiles and is expelled from the spindle chamber 10 through the pump outlet 13 .
  • a motor housing 3 adjoins the spindle housing on the pressure side of the spindle chamber 10 .
  • the motor housing 3 has a flange section 35 which is designed to match a flange section 15 of the spindle housing 1 .
  • the flange connection is sealed with a gasket.
  • a separate motor chamber 30 is formed in the motor housing 3, in which the dry-running electric motor 4 and electronics, in particular power electronics (not shown) for switching the electrical power on the electric motor 4, are accommodated. an open one
  • the end of motor chamber 30 is closed off by a motor cover (not shown).
  • a collar-shaped bearing seat 32 with a through-opening in a front-side boundary of the motor chamber 30 is formed in the motor housing 3 .
  • a common shaft bearing 23 of the electric motor 4 and the driven screw spindle 2a is fitted in the bearing seat 32 .
  • a shaft seal 34 is fitted into the bearing seat 32, which seals the motor chamber 30 from liquid ingress.
  • the dry electric motor 4 is an inner rotor type having an inner rotor 42 and an outer stator 41.
  • the rotor 42 is coupled to the driven screw rod 2a.
  • the stator 41 includes field coils that are controlled by the power electronics and supplied with electrical power.
  • the stator 41 of the electric motor 4 is in thermal contact with an inner peripheral surface and with a front boundary surface of the motor chamber 30 , so that waste heat from the field coils of the stator 41 is transferred to the motor housing 3 .
  • the motor case 3 is made of a metallic material having good thermal conductivity, such as aluminum alloy casting, and is formed as a one-piece cast molding.
  • a heat transfer section 31 of the motor housing 3 extends in an axial section between the motor chamber 30 and the flange section 35.
  • the pump outlet 13 is arranged in the form of a radially discharging pressure connection between the motor chamber 30 and the spindle chamber 10.
  • a delivery flow chamber 33 through which the liquid delivery medium flows is formed within the heat transfer section 31 .
  • the delivery flow chamber 33 establishes a connection between the pressure side of the spindle chamber 10 and the pump outlet 13 for the delivery flow of the pump.
  • the delivery flow chamber 33 surrounds the collar-shaped bearing seat 32 and guides the pressurized, liquid delivery medium to the end boundary of the motor chamber 30, with which the stator 41 is in thermal contact.
  • the heat transfer section 31 represents that area of the thermally conductive material volume on the motor housing 3 which is decisively involved in dissipating waste heat from the motor chamber 30 into the flow.
  • the inner surface of the pump outlet 13, the inner surface of the flow chamber 33 and the surface of the bearing seat 32 each contribute to an increase in the thermal contact area between the motor chamber 30 and the flow within the heat transfer section 31.
  • a temperature difference between a coolant and the engine chamber 30 is limited by the optimized heat transfer.
  • a critical component temperature of the electric drive at which overheating damage to the winding insulation of the stator 41 or the electronics can occur, is reliably prevented even under high loads with a high operating temperature of a coolant circuit.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Details Of Reciprocating Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)

Claims (9)

  1. Pompe de refroidissement à broches de vis électrique destinée à stimuler un circuit de refroidissement, présentant :
    un logement de broche (1) avec un compartiment de broche (10) dans lequel sont reçues au moins deux broches de vis (2a, 2b) ;
    une admission de pompe (11) et une évacuation de pompe (13) pour guider un courant d'alimentation à travers le compartiment de broche (10) ;
    un logement de moteur (3) qui est agencé axialement dans le voisinage du logement de broche (1) ;
    caractérisée en ce que
    le logement de moteur (3) comprend un compartiment de moteur (30) dans lequel est agencé un moteur électrique (4) sec délimité au courant d'alimentation ; et
    le logement de moteur (3) présente une section de transfert de chaleur (31) traversée par le courant d'alimentation, qui est agencée entre le compartiment de moteur (30) et une limite de composante du logement de moteur (3) vers le logement de broche (1).
  2. Pompe de refroidissement à broches de vis électrique selon la revendication 1, dans laquelle
    la section de transfert de chaleur (31) comprend en outre l'évacuation de pompe (13).
  3. Pompe de refroidissement à broches de vis électrique selon la revendication 1 ou 2, dans laquelle
    la section de transfert de chaleur (31) comprend un compartiment de courant d'alimentation (33) qui produit une liaison entre une délimitation frontale du compartiment de moteur (30) et le compartiment de broche (10).
  4. Pompe de refroidissement à broches de vis électrique selon l'une des revendications précédentes, dans laquelle
    la section de transfert de chaleur (31) comprend un siège de palier (32) pour un palier d'arbre (23), lequel palier d'arbre est agencé entre le moteur électrique (4) et les broches de vis (2a, 2b).
  5. Pompe de refroidissement à broches de vis électrique selon l'une des revendications précédentes, dans laquelle
    une électronique pour le moteur électrique (4) est également agencée dans le compartiment de moteur (30).
  6. Pompe de refroidissement à broches de vis électrique selon l'une des revendications précédentes, dans laquelle
    un stator (41) et/ou une électronique du moteur électrique (4) dans le logement de moteur (3) sont en contact avec une délimitation frontale du compartiment de moteur (30).
  7. Pompe de refroidissement à broches de vis électrique selon l'une des revendications précédentes, dans laquelle
    la section de transfert de chaleur (31) est formée en une seule pièce avec le logement de moteur (3).
  8. Pompe de refroidissement à broches de vis électrique selon l'une des revendications précédentes, dans laquelle
    le logement de broche (1) est formé en une seule pièce.
  9. Pompe de refroidissement à broches de vis électrique selon l'une des revendications précédentes, dans laquelle
    au niveau de la limite de composante entre le logement de moteur (3) et le logement de broche (1), une liaison à bride est formée à partir d'une section de bride (35) du logement de moteur (3) et d'une section de bride (15) du logement de broche (1).
EP19817281.9A 2019-02-12 2019-12-09 Pompe à vis à liquide de refroidissement électrique Active EP3924624B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102019103470.1A DE102019103470A1 (de) 2019-02-12 2019-02-12 Elektrische Schraubenspindel-Kühlmittelpumpe
PCT/EP2019/084161 WO2020164776A1 (fr) 2019-02-12 2019-12-09 Pompe à vis à liquide de refroidissement électrique

Publications (2)

Publication Number Publication Date
EP3924624A1 EP3924624A1 (fr) 2021-12-22
EP3924624B1 true EP3924624B1 (fr) 2023-04-19

Family

ID=68835242

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19817281.9A Active EP3924624B1 (fr) 2019-02-12 2019-12-09 Pompe à vis à liquide de refroidissement électrique

Country Status (6)

Country Link
US (1) US20220099088A1 (fr)
EP (1) EP3924624B1 (fr)
CN (1) CN113227580B (fr)
BR (1) BR112021012370A2 (fr)
DE (1) DE102019103470A1 (fr)
WO (1) WO2020164776A1 (fr)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102019118094A1 (de) * 2019-07-04 2021-01-07 Nidec Gpm Gmbh Temperierungsvorrichtung für ein Batteriespeichermodul
DE102019118086A1 (de) * 2019-07-04 2021-01-07 Nidec Gpm Gmbh Integrierte Schraubenspindel-Kühlmittelpumpe
IT202100019787A1 (it) * 2021-07-26 2023-01-26 Fluid O Tech Srl Pompa a viti perfezionata, particolarmente per sistemi di raffreddamento.
DE102021133106A1 (de) * 2021-12-14 2023-06-15 Leistritz Pumpen Gmbh Schraubenspindelpumpe
DE102021133099A1 (de) * 2021-12-14 2023-06-15 Leistritz Pumpen Gmbh Schraubenspindelpumpe

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DE3245973A1 (de) * 1982-12-11 1984-06-14 Allweiler Ag, 7760 Radolfzell Motorpumpenaggregat
FR2544459B1 (fr) * 1983-04-14 1987-04-30 Zimmern Bernard Procede pour lubrifier les roulements d'un compresseur, et compresseur frigorifique utilisant ce procede
US5222874A (en) * 1991-01-09 1993-06-29 Sullair Corporation Lubricant cooled electric drive motor for a compressor
DE19745616A1 (de) * 1997-10-10 1999-04-15 Leybold Vakuum Gmbh Gekühlte Schraubenvakuumpumpe
KR100386753B1 (ko) * 1998-03-23 2003-06-09 다이코 기카이 고교 가부시키가이샤 드라이 진공펌프
WO2000008338A1 (fr) * 1998-08-06 2000-02-17 Automotive Motion Technology Limited Pompe entrainee par un moteur
BE1013944A3 (nl) * 2001-03-06 2003-01-14 Atlas Copco Airpower Nv Watergeinjecteerde schroefcompressor.
DE102005025816B4 (de) * 2005-06-02 2010-06-02 Joh. Heinr. Bornemann Gmbh Schraubenspindelpumpe
CN101265900A (zh) * 2008-04-23 2008-09-17 王法荣 屏蔽电泵
EP2313657A1 (fr) * 2008-07-18 2011-04-27 Ralf Steffens Refroidissement d'une pompe à vis
JP5334801B2 (ja) * 2009-11-04 2013-11-06 株式会社神戸製鋼所 ２段スクリュ圧縮機および冷凍装置
CN101975160B (zh) * 2010-11-16 2014-12-03 上海维尔泰克螺杆机械有限公司 双螺杆液体泵
CN201991766U (zh) * 2011-03-30 2011-09-28 上海沪石石油机械有限公司 一种三螺杆输油泵
BE1020311A3 (nl) * 2012-02-28 2013-07-02 Atlas Copco Airpower Nv Schroefcompressor.
WO2014138519A1 (fr) 2013-03-07 2014-09-12 Ti Group Automotive Systems, L.L.C. Élément d'accouplement pour pompe à vis
DE102015101443B3 (de) 2015-02-02 2016-05-12 Leistritz Pumpen Gmbh Kraftstoffpumpe
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DE102017210771B4 (de) 2017-06-27 2019-05-29 Continental Automotive Gmbh Schraubenspindelpumpe, Kraftstoffförderaggregat und Kraftstofffördereinheit

Also Published As

Publication number Publication date
EP3924624A1 (fr) 2021-12-22
CN113227580B (zh) 2023-06-27
US20220099088A1 (en) 2022-03-31
DE102019103470A1 (de) 2020-08-13
WO2020164776A1 (fr) 2020-08-20
BR112021012370A2 (pt) 2021-08-31
CN113227580A (zh) 2021-08-06

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