US20220099088A1 - Electrical screw spindle coolant pump - Google Patents

Electrical screw spindle coolant pump Download PDF

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Publication number
US20220099088A1
US20220099088A1 US17/428,582 US201917428582A US2022099088A1 US 20220099088 A1 US20220099088 A1 US 20220099088A1 US 201917428582 A US201917428582 A US 201917428582A US 2022099088 A1 US2022099088 A1 US 2022099088A1
Authority
US
United States
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.)
Abandoned
Application number
US17/428,582
Other languages
English (en)
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
Original Assignee
Nidec GPM GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Nidec GPM GmbH filed Critical Nidec GPM GmbH
Assigned to NIDEC GPM GMBH reassignment NIDEC GPM GMBH ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: PAWELLEK, FRANZ, Döhler, Daniel
Publication of US20220099088A1 publication Critical patent/US20220099088A1/en
Abandoned 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 the screw pump type for delivery of a coolant circulation or the like, in particular for delivering corrosive, liquid media.
  • Screw pumps are displacement pumps which permit high pressures and high volumetric efficiency. They do not offer adjustment of the geometry in a manner independent of speed but they do comprise a robust rotary piston mechanism which is not sensitive to fouling and which operates without delicate elements such as stop valves or the like. Consequently, mechanically driven screw pumps have to date predominantly been used in large-scale applications such as e.g. oil pumps in stationary installations or ships engines in which they run with relatively constant operating points.
  • US 2018/0216614 A1 describes a screw pump which is provided as a fuel pump.
  • a cover with an axial outlet is attached to a housing of the screw pump.
  • the electric motor is received in an outlet chamber of the cover and fuel flows through it before it leaves the outlet.
  • 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 it leaves the pressure-side outlet.
  • WO 2014/138519 A1 describes an electric liquid pump of the screw type.
  • the liquid which flows through an inlet and an outlet also surrounds the motor.
  • a fuel is mentioned as the liquid.
  • a flange plane which is shown in the illustrated construction between a motor-side housing part and a pump-side housing part, extends between the motor and a pump-side outlet.
  • the above-mentioned pumps cannot be transferred to an application as an electric water pump, in particular not as an electric coolant pump.
  • a liquid medium to be delivered, such as a coolant would corrosively damage the exposed components of the electric motor, in particular the coil windings of the stator.
  • U.S. Pat. No. 6,371,744 B1 describes an electric vacuum pump of the screw type.
  • the screw spindles are driven by an electric motor which is arranged in a separate housing.
  • said vacuum pump could not be transferred to an application as an electric coolant pump.
  • sufficient cooling of a dry-running electric motor could not be ensured.
  • a target temperature for a coolant can be in the vicinity of the boiling temperature of the coolant. In this case, in continuous operation, overheating damage to electric or electronic components would occur.
  • Another, partial aspect of the object is further to provide a corresponding technical solution such that it can also be inexpensively produced in large numbers by mass production.
  • the electric screw coolant pump in accordance with the invention for delivering a coolant circulation is characterised in particular in that a motor housing comprises a motor chamber, in which a dry-running electric motor is arranged in such a manner that it is delimited with respect to the delivery flow; and that the motor housing comprises a heat transfer section, through which the delivery flow flows, arranged between the motor chamber and a component boundary between the motor housing and a spindle housing.
  • the invention provides a screw pump as a coolant pump.
  • the invention provides a screw pump as an electric liquid pump which is driven by a dry-running electric motor.
  • the invention provides a screw 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 medium to be delivered is provided.
  • the invention permits a coolant pump to be produced with a high level of power density.
  • the screw pump provides the high delivery pressure of a displacement pump but with relatively low pulsation, similar to a centrifugal pump.
  • the screw pump permits universal installations and applications.
  • the electric screw coolant pump in accordance with the invention is suitable e.g. 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 ducts 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.
  • a region protected from the liquid of the delivery flow is provided and so the electric drive is not exposed to corrosive influences.
  • a liquid-carrying region on the motor housing is provided, which enlarges an internal thermal contact surface with the coolant.
  • Waste heat from electric power dissipation can be effectively carried away from the pump by a heat exchange at the thermal contact surface, thus produced, of the heat-conducting motor housing and convection of the delivery flow, even when there is a small temperature difference between the electric drive and the coolant.
  • the enlargement of the thermal contact surface is achieved without an increased level of complexity in the structure, as in the form of surface-enlarging structures, flow resistance means or the like.
  • the motor housing is designed as a cast part during product development.
  • the changed component boundary can be produced on the pump construction in accordance with the invention without considerable outlay or increase in manufacturing costs.
  • substantially no disadvantageous increase in the overall dimensions of the pump arises despite having an increased axial dimension for the motor housing.
  • the heat transfer section can further comprise the pump outlet.
  • the flow cross-section of the entire delivery flow can be channelled past the motor chamber.
  • the internal surface of the pump outlet at the heat transfer section further enlarges the thermal contact surface of the heat-conducting motor housing with the delivery flow to a considerable extent.
  • the heat transfer section can comprise a delivery flow chamber which produces a connection between the frontal delimitation of the motor chamber and the spindle chamber.
  • the heat transfer section can comprise a bearing seat for a shaft bearing, which is arranged between the electric motor and the screw spindles.
  • the surface of the bearing seat in the heat transfer section in turn enlarges the thermal contact surface of the heat-conducting motor housing with the delivery flow.
  • the integration of a shaft bearing in the axial region of the heat transfer section is favourable to a compact construction for the pump.
  • an electronic system for the electric motor can also be arranged in the motor chamber.
  • a further heat source is therefore incorporated into the inventive cooling of the electric drive.
  • the power dissipation from power electronics is also discharged via the delivery flow.
  • a stator and/or an electronic system of the electric motor in the motor housing can be in contact with a frontal delimitation of the motor chamber. Therefore, the smallest possible heat transfer portion of the heat-conducting motor housing between the electric heat sources in the motor chamber and the delivery flow is ensured.
  • the heat transfer section can be formed integrally with the motor housing. In this way, an optimised heat transfer portion without boundary surfaces or joints in the material and the lowest possible production costs for the motor housing are ensured.
  • the spindle housing can be formed as one piece.
  • the shifting of the component boundary between the motor housing and the spindle housing produces an open cross-section for the spindle chamber. In this way, both for assembly of the pump and also for production of the moulded body of the spindle housing no division into two housing halves is required.
  • the one-piece design of the spindle housing ensures a joint-free internal contour for the spindle chamber without the need for post-processing.
  • the internal contour of the spindle chamber can be produced simply and precisely by bores.
  • the spindle housing can comprise the pump inlet.
  • the spindle housing is designed as a cast part during product development. Consequently, by integration of the pump inlet, the number of components of the pump construction in accordance with the invention can be reduced without considerable outlay.
  • a flange joint consisting 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 joint permits a preferred screw connection for assembly of the two housing components, while a corresponding flange plane allows different types of seal.
  • FIG. 1 shows a schematic sectional view through a screw coolant pump according to one embodiment of the invention.
  • screw pump is understood to mean skew rotary piston pumps with a thread pitch for displacement of the medium to be delivered.
  • Such types of pump generally comprise a driven screw spindle 2 a and at least one further screw spindle 2 b which is in coupled motion therewith via engagement of the toothing.
  • a driven screw spindle 2 a and a screw spindle 2 b in coupled motion are received in a rotatably mounted manner in a spindle chamber 10 of the spindle housing 1 .
  • the spindle chamber 10 has a cross-sectional contour in the form of a so-called figure-of-eight housing, i.e. it is formed by two bores in the pump housing 1 with overlapping radii in order to ensure engagement of the screw spindles 2 a, 2 b.
  • the driven screw spindle 2 a is connected to an electric motor 4 .
  • a pressure side of the spindle chamber 10 which communicates with a pump outlet 13 in the form of a pressure connection is located on the drive side of the screw spindles 2 a, 2 b.
  • a suction side of the spindle chamber 10 is located on the other side of the screw spindles 2 a, 2 b opposite the electric motor 4 .
  • the suction side of the spindle chamber 10 communicates with a pump inlet 11 in the form of a suction connection.
  • a liquid medium to be delivered or a coolant is drawn into the spindle chamber 10 from a coolant circulation through the pump inlet 11 on the suction side.
  • a rotational movement of engaged screw profiles of the rotating screw spindles 2 a, 2 b generates a negative pressure on the suction side of the spindle chamber 10 and a positive pressure on the opposing pressure side of the spindle chamber 10 .
  • the medium to be delivered is delivered by continuous displacement along a screw pitch of the engaged screw profiles and ejected 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 comprises a flange section 35 which is formed to match a flange section 15 of the spindle housing 1 .
  • the flange joint is sealed by a seal.
  • a separated motor chamber 30 is formed in the motor housing 3 , in which chamber the dry-running electric motor 4 and an electronic system, in particular power electronics (not shown), for switching the electric power at the electric motor are received.
  • An open end of the motor chamber 30 is closed by a motor cover (not shown).
  • a collar-shaped bearing seat 32 with a though-opening in a frontal delimitation of the motor chamber 30 is formed in the motor housing 3 .
  • a common shaft bearing 23 of the electric motor 4 and of the driven screw spindle 2 a is fitted in the bearing seat 32 . Upstream of the shaft bearing 23 , a shaft seal 34 is fitted into the bearing seat 32 and seals the motor chamber 30 against ingress of liquid.
  • the dry-running electric motor 4 is of the internal rotor type with an internal rotor 42 and an external stator 41 .
  • the rotor 42 is coupled to the driven screw spindle 2 a.
  • the stator 41 comprises field coils which are actuated by the power electronics and supplied with electric power.
  • the stator 41 of the electric motor 4 is in thermal contact with an internal peripheral surface and with a frontal boundary surface of the motor chamber 30 , and so waste heat from the field coils of the stator 41 is transferred to the motor housing 3 .
  • the motor housing 3 consists of a metallic material with a good level of heat conductivity, such as an aluminium cast alloy, and is formed as a one-piece cast part.
  • 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 in the form of a radially discharging pressure connection is arranged between the motor chamber 30 and the spindle chamber 10 .
  • a delivery flow chamber 33 is formed within the heat transfer section 31 and has the liquid medium to be delivered flowing through it.
  • the delivery flow chamber 33 produces a connection for the delivery flow of the pump between the pressure side of the spindle chamber 10 and the pump outlet 13 .
  • the delivery flow chamber 33 surrounds the collar-shaped bearing seat 32 and carries the pressurised liquid medium to be delivered to the frontal delimitation of the motor chamber 30 , with which the stator 41 is in thermal contact.
  • the heat transfer section 31 constitutes the region of the heat-conducting material volume on the motor housing 3 which is definitively involved in the dissipation of waste heat from the motor chamber 30 into the delivery flow.
  • the internal surface of the pump outlet 13 , the internal surface of the delivery flow chamber 33 and the surface of the bearing seat 32 each contribute to enlargement of the thermal contact surface between the motor chamber 30 and the delivery flow within the heat transfer section 31 .
  • the optimised heat transfer limits any temperature difference between a coolant and the motor chamber 30 . Consequently, even under high loading with a high operating temperature in a coolant circulation, a critical component temperature of the electric drive, at which overheating damage can occur on the winding insulations of the stator 41 or the electronic system, is reliably prevented.

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)
US17/428,582 2019-02-12 2019-12-09 Electrical screw spindle coolant pump Abandoned US20220099088A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102019103470.1 2019-02-12
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 (1)

Publication Number Publication Date
US20220099088A1 true US20220099088A1 (en) 2022-03-31

Family

ID=68835242

Family Applications (1)

Application Number Title Priority Date Filing Date
US17/428,582 Abandoned US20220099088A1 (en) 2019-02-12 2019-12-09 Electrical screw spindle coolant pump

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)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US12230777B2 (en) 2019-07-04 2025-02-18 Nidec Gpm Gmbh Temperature control device for a battery bank module

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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.
DE102021133099A1 (de) * 2021-12-14 2023-06-15 Leistritz Pumpen Gmbh Schraubenspindelpumpe
DE102021133112A1 (de) * 2021-12-14 2023-06-15 Leistritz Pumpen Gmbh Schraubenspindelpumpe
DE102021133109A1 (de) * 2021-12-14 2023-06-15 Leistritz Pumpen Gmbh Schraubenspindelpumpe
DE102021133106A1 (de) * 2021-12-14 2023-06-15 Leistritz Pumpen Gmbh Schraubenspindelpumpe
EP4474650B1 (fr) 2023-06-09 2026-03-25 Illinois Tool Works Inc. Pompe à vis et ses composants
US12533995B2 (en) 2023-08-31 2026-01-27 Illinois Tool Works Inc. Battery electric vehicle temperature-regulation system

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US6499966B1 (en) * 1998-08-06 2002-12-31 Automative Motion Technology, Ltd. Motor driven pump
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US20180172002A1 (en) * 2012-02-28 2018-06-21 Atlas Copco Airpower, Naamloze Vennootschap Screw compressor

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Publication number Priority date Publication date Assignee Title
US12230777B2 (en) 2019-07-04 2025-02-18 Nidec Gpm Gmbh Temperature control device for a battery bank module

Also Published As

Publication number Publication date
CN113227580A (zh) 2021-08-06
EP3924624B1 (fr) 2023-04-19
BR112021012370A2 (pt) 2021-08-31
EP3924624A1 (fr) 2021-12-22
WO2020164776A1 (fr) 2020-08-20
DE102019103470A1 (de) 2020-08-13
CN113227580B (zh) 2023-06-27

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