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US20090155100A1 - Fluid pump - Google Patents

Fluid pump Download PDF

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Publication number
US20090155100A1
US20090155100A1 US12/093,405 US9340506A US2009155100A1 US 20090155100 A1 US20090155100 A1 US 20090155100A1 US 9340506 A US9340506 A US 9340506A US 2009155100 A1 US2009155100 A1 US 2009155100A1
Authority
US
United States
Prior art keywords
housing part
pressure
pump
motor housing
internal combustion
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
US12/093,405
Other languages
English (en)
Inventor
Albert Genster
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.)
Pierburg GmbH
Original Assignee
Pierburg 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 Pierburg GmbH filed Critical Pierburg GmbH
Assigned to PIERBURG GMBH reassignment PIERBURG GMBH ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: GENSTER, ALBERT
Publication of US20090155100A1 publication Critical patent/US20090155100A1/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
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/52—Casings; Connections of working fluid for axial pumps
    • F04D29/54—Fluid-guiding means, e.g. diffusers
    • F04D29/548—Specially adapted for liquid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D1/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D1/04—Helico-centrifugal pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • 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
    • F04D13/0626—Details of the can

Definitions

  • the invention is directed to a fluid pump for internal combustion engines, comprising an electric motor with a rotor arranged in a motor housing and a stator, the rotor being arranged on a drive shaft at least in a manner secured against rotation, an impeller fastened on the drive shaft, at least one set of guide vanes arranged behind the impeller in the flow direction of the fluid to be conveyed, and a pump housing enclosing the motor housing, the impeller and the guide vanes and at which a pressure port and an intake port are arranged opposite the axial ends.
  • Fluid pumps for internal combustion engines are used especially as coolant pumps in the cooling circuit.
  • a direct coupling with the engine speed existed and the pumps were driven by belt or chain drives
  • more recent engines increasingly use electric variable speed coolant pumps with a can, so as to realize a modern thermal management.
  • an excessive delivery rate can be prevented, so that, for example, the internal combustion engine can be heated up faster after a cold start.
  • the delivery rate can be controlled according to the actually required cooling capacity.
  • Such a pump is known, for example, from MTZ No. 11, vol. 2005 (p. 872-877).
  • This electric coolant pump comprises an EC motor as the drive unit and has a pump head with an axial inlet and a tangential outlet.
  • the components and especially the housing parts used therein are rather large for the power input of the pump, since a relatively large drive motor has to be used.
  • US 2002/0106290 A1 discloses an electric fluid pump of semi-axial construction, whereby, with the same power input to the electric motor, the electric motor can be made smaller to obtain higher speeds, so that the same delivery rate can be obtained with a more compact structure. It comprises a completely enclosed electromotor with a guide vanes provided at the outer side thereof. However, behind the guide vanes, seen in the flow direction, obstacles are formed that hinder the establishing of the electric contacting to the electronic unit. On the impeller side, the entire motor is sealed with gaskets from the environment. It is at least debatable whether such a sealing at the rotating parts is sufficient.
  • the pump housing is bipartite and has various steps and through holes for electric contacting. Depending on the desired maximum delivery rate, different electric motors and housings must be designed.
  • This object is achieved by providing a pressure-side motor housing part with a conduction device.
  • This conduction device allows to obtain an almost completely irrotational flow so that the kinetic energy of the tangential component of the flow velocity is converted into pressure energy with low friction losses. This increases the efficiency of the fluid pump. Thus, in order to obtain an unaltered delivery rate, it is also possible to reduce the overall size of the electric motor.
  • the conduction device is formed by recirculation vanes manufactured integrally with the pressure-side motor housing part and formed on the surface thereof, so that no additional components are required and an irrotational flow with little loss of energy is guaranteed.
  • the recirculation vanes serve to convert the tangential flow component into an axial flow component without any significant pressure losses. The efficiency is increased and the number of components is reduced.
  • the pressure-side motor housing part is tapered in the flow direction and surrounded by a correspondingly shaped pressure-side pump housing part.
  • the radial ends of the recirculation vanes are delimited by the pump housing, so that it is reliably prevented that the vanes are flown over.
  • the pressure-side motor housing part is adapted to be slid into a receiving opening of an axially adjoining motor housing part by slipping the pressure-side pump housing part onto the pressure-side motor housing part, with interposition of a gasket, wherein the pressure-side motor housing part is fixed by fastening the pressure-side pump housing part at a pump housing part situated radially outward with respect to the axially adjoining motor housing part. Accordingly, no fastening elements have to be used to fasten the pressure-side motor housing part. The fastening of the pump housing part alone guarantees for a tight fastening of the motor housing, so that the assembly effort is reduced.
  • the pressure-side pump housing part has a flange via which the fluid pump can be fastened to an internal combustion engine.
  • the pressure port can be made integrally with the flange, so that the fluid pump can be flange-mounted directly on a motor housing, for example, without additional intermediate lines.
  • a plurality of fluid pumps are connected in series via a flange connection, the flanges being formed at the pressure-side pump housing part of the first pump and a suction-side pump housing part of a downstream pump. It is possible to provide a series connection without additional components, allowing to realize a higher required maximum volume flow. This becomes possible especially because of the irrotational flow in the outlet port caused by the conduction device. Thus, it is possible, in a restricted package space, to achieve a different delivery flow with different motor sizes, without any redesigning and without changing the components. Thereby, costs can be reduced.
  • a fluid pump that supplies an irrotational flow at the outlet and operates with negligible pressure losses by friction and the like. This increases the efficiency, since a large part of the kinetic energy is actually converted into pressure energy.
  • a series connection allows to obtain various delivery rates with the same components in a compact space.
  • the FIGURE is a side elevational sectional view of a fluid pump according to the present invention.
  • the fluid pump illustrated in the FIGURE which is particularly suited as a coolant pump in internal combustion engines, is driven by an electronically commuted electric motor 1 , formed by a stator 2 and a rotor 4 arranged on a drive shaft 3 .
  • the axial end of the drive shaft 3 is provided with an impeller 5 that is realized in a semi-axial construction and by whose rotation the fluid to be conveyed, especially a coolant, is conveyed substantially axially from an intake port 6 through the fluid pump to a pressure port 7 .
  • the electric motor 1 is arranged in a motor housing formed by a first, suction-side motor housing part 8 and a second, pressure-side motor housing part 9 .
  • the drive shaft 3 on which the impeller 5 is arranged, is passed through the suction-side motor housing part 8 .
  • the suction-side motor housing part 8 has a bore 10 with a first bearing 11 being arranged therein for supporting the drive shaft 3 .
  • Behind the first bearing 11 seen from the suction side, an ceramic axial sliding bearing 12 as well as a rubber sleeve 13 and a spacer 14 are situated.
  • This assembly allows to achieve a sufficiently vibration-damped support of the impeller side of the drive shaft 3 of the electric motor 1 .
  • the spacer serves to widen the distance between the first bearing 11 and a second bearing 15 , whereby an angular error caused when making the bore 10 for receiving the bearings can be compensated better.
  • a rotor pack 16 is arranged on the shaft, comprising axially extending slits for receiving magnets 17 corresponding with a stator coil 18 in a manner known per se.
  • the rotor 4 is delimited axially and radially by an enclosure 19 .
  • the stator coil 18 is wound on an insulating body 20 and axially delimits a stator pack 21 in a manner known per se.
  • this stator pack 21 is positively connected with a magnetic yoke 22 .
  • This magnetic yoke 22 rests against an abutment 23 formed on an inner surface of the first suction-side motor housing part 8 .
  • the rotor 4 is separated from the stator 2 by a can 24 resting on the suction side of the pump in a corresponding receiving opening 25 of the suction-side motor housing part 8 , and whose opposite axial end is arranged, in turn, in a corresponding receiving opening 26 of the pressure-side motor housing part 9 .
  • the stator 2 with its sensitive coil 18 is thus situated in a dry space separated by the two motor housing parts 8 and 9 and the can 24 .
  • a closure member 27 in which the second bearing 15 is arranged to support the drive shaft 3 .
  • This closure member 27 is secured axially by the pressure-side motor housing part 9 , which, with the interposition of a gasket 28 , is arranged in a receiving opening 29 of the suction-side motor housing part 8 .
  • the stator coil 18 is contacted, via a bore 30 , in the radial direction through the pressure-side motor housing part 9 .
  • this bore is made through supporting ribs 31 , as known in prior art, which ribs are required to provide a pump housing with sufficient strength and for mounting the same.
  • the supporting ribs 31 are sufficiently wide and are shaped similar to an airfoil, so that no constriction of the cross section is formed.
  • an electric contact element can be passed through the bore 30 to an electronic unit (also not illustrated) for controlling the motor 1 .
  • the supporting ribs 31 are formed such that they simultaneously serve as the guide vanes, so that no additional guide vanes is needed immediately behind the impeller 5 .
  • This allows for a simple manufacturing of the suction-side motor housing 8 as one piece, with the supporting ribs and a cylindrical radially outer pump housing part 32 .
  • This pump housing part 32 encloses the radially inner motor housing part 8 , as well as the entire electric motor 1 .
  • the suction-side pump-housing part 33 flaring in the direction of flow, comprises the intake port 6 configured as a cylindrical section 35 , as well as an adjoining flaring section 46 .
  • the semi-axial impeller 5 of the fluid pump is arranged in the transition 37 between the first section 35 and the second section 36 .
  • the flaring section 36 is adjoined by another short cylindrical section 38 of larger diameter to achieve a smooth transition to the cylindrical pump housing part 32 .
  • the identical pump housing parts 33 , 34 are formed with grooves 39 into which radial ends 40 of recirculation vanes 41 engage.
  • These recirculation vanes 41 serve as the conducting device 42 by means of which a completely irrotational flow is obtained behind the pressure port 7 .
  • This conducting device 42 is formed on a surface 43 of the pressure-side motor housing part 9 and becomes necessary, because the supporting ribs 31 serving as guide vanes are made rather short and a completely irrotational flow is usually not achieved in this part of the fluid pump.
  • the pressure-side motor housing part 9 can be made of plastic material, whereas the suction-side motor housing part should possible be made of aluminum and is thus more expensive. Such a configuration of the guide vanes in this portion would require a rather expensive production method, whereas the conduction device at the plastic housing part 9 is simple and economic to manufacture.
  • the grooves 39 also define the position of the pressure-side pump housing part 34 with respect to the pressure-side motor housing part 9 .
  • the pressure-side pump housing part 34 presses the motor housing part 9 against the motor housing part 8 or into the receiving openings 29 of the motor housing part 8 . Further, the motor housing part 9 is thereby pressed against the closure member 27 and the can 24 , respectively, so that no additional fastening of the two motor housing parts 8 , 9 is required.
  • the rotation of the impeller 5 formed by a plurality of impeller vanes 44 conveys the fluid to be conveyed, in particular the coolant, through the space between the pump housing 32 , 33 , 34 and the motor housing 8 and 9 , the fluid flows past the supporting ribs 31 , where a part of the flow rotation is already removed due to their function as guide vanes, and it flows on through the conduction device 42 where the still existing rotation of the flow is removed completely so that the energy spent is converted as completely as possible into pressure energy and thus into an axial flow without incurring high friction losses.
  • This semi-axial pump is especially characterized in that it can be of a particularly compact structure, since with the same power input the same delivery rate can be obtained though with a smaller motor size and an increased speed when compared with known pumps. This is achieved especially by the extremely reduced pressure losses in such a design, but also by the semi-axial construction.
  • suction-side pump housing part 33 it is also conceivable, due to the simplicity of the suction-side pump housing part 33 , in particular, to form the same integrally with valve housing parts so that the pump housing parts 33 could comprise a receptacle for a bypass or an integrated heat valve. Parts of the housing of an annular slide valve could also be made integrally with the suction-side pump housing part 33 .

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Fluid-Driven Valves (AREA)
US12/093,405 2005-11-10 2006-10-10 Fluid pump Abandoned US20090155100A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102005054027A DE102005054027A1 (de) 2005-11-10 2005-11-10 Fluidpumpe
DE102005054.027.9 2005-11-10
PCT/EP2006/009763 WO2007054171A1 (de) 2005-11-10 2006-10-10 Fluidpumpe

Publications (1)

Publication Number Publication Date
US20090155100A1 true US20090155100A1 (en) 2009-06-18

Family

ID=37663301

Family Applications (1)

Application Number Title Priority Date Filing Date
US12/093,405 Abandoned US20090155100A1 (en) 2005-11-10 2006-10-10 Fluid pump

Country Status (7)

Country Link
US (1) US20090155100A1 (de)
EP (1) EP1945955B1 (de)
JP (1) JP2009515086A (de)
CN (1) CN101365884B (de)
AT (1) ATE460587T1 (de)
DE (2) DE102005054027A1 (de)
WO (1) WO2007054171A1 (de)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20050248081A1 (en) * 2004-05-05 2005-11-10 Heidelberger Druckmaschinen Aktiengesellschaft Configuration for the transport and simultaneous alignment of sheets
US20130028760A1 (en) * 2011-07-29 2013-01-31 Lin Chih M Pump motor combination
US20160201623A1 (en) * 2013-09-17 2016-07-14 Denso Corporation Liquid pump

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102014202564B4 (de) 2014-02-12 2025-06-12 Volkswagen Aktiengesellschaft Fluidpumpe und Kühlmittelfördereinrichtung für einen Verbrennungsmotor mit einer solchen
DE102014114801B4 (de) * 2014-10-13 2017-08-31 Lutz Pumpen Gmbh Strömungsmaschine mit halbaxialem Laufrad
CN114930689B (zh) * 2019-10-30 2025-10-17 福斯私人有限公司 具有集成马达或发电机的模块及多级设备

Citations (23)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1949796A (en) * 1931-08-29 1934-03-06 Himmelwerk Ag Pump or impeller
US2824520A (en) * 1952-11-10 1958-02-25 Henning G Bartels Device for increasing the pressure or the speed of a fluid flowing within a pipe-line
US2855141A (en) * 1955-11-25 1958-10-07 Jacobus C Van Rijn Two-piece cantilever fan and motor
US2968249A (en) * 1958-09-04 1961-01-17 Borg Warner Axial flow apparatus
US3102679A (en) * 1962-01-15 1963-09-03 Loren Cook Company Centrifugal impeller units
US3135212A (en) * 1962-03-29 1964-06-02 Symington Wayne Corp Submersible pump
US3244106A (en) * 1963-09-30 1966-04-05 North American Aviation Inc High pressure pumping device
US3398694A (en) * 1966-08-11 1968-08-27 Marine Constr & Design Co Submersible pump device for net brailing
US3826595A (en) * 1973-03-07 1974-07-30 Lucas Industries Ltd Electrically driven pump
US3836291A (en) * 1971-11-29 1974-09-17 Bosch Gmbh Robert Pump-and-motor unit, particularly for supplying fuel
US4213745A (en) * 1978-09-11 1980-07-22 Roberts Samuel A Pump for central heating system
US5350281A (en) * 1993-01-26 1994-09-27 Sundstrand Corporation Fan with secondary air passage for motor cooling
US5487644A (en) * 1987-02-13 1996-01-30 Ishigaki Mechanical Industry Co., Ltd Pump having a single or a plurality of helical blades
US5494418A (en) * 1992-04-14 1996-02-27 Ebara Corporation Pump casing made of sheet metal
US5567133A (en) * 1993-07-16 1996-10-22 Ebara Corporation Canned motor and pump employing such canned motor
US5674056A (en) * 1993-12-28 1997-10-07 Ebara Corporation Motor pump assembly
US6056518A (en) * 1997-06-16 2000-05-02 Engineered Machined Products Fluid pump
US6135098A (en) * 1998-10-06 2000-10-24 Engineered Machine Products, Inc. Flow-through controllable air charger
US6175173B1 (en) * 1998-09-15 2001-01-16 Wilo Gmbh Tube pump
US20020106290A1 (en) * 2001-02-05 2002-08-08 Engineered Machined Products, Inc. Electronic fluid pump
US20030021683A1 (en) * 2001-03-14 2003-01-30 Capone Christopher D. Touch down of blood pump impellers
US20040013547A1 (en) * 2002-07-17 2004-01-22 Engineered Machined Products, Inc. Electronic fluid pump
US20040109762A1 (en) * 2002-12-10 2004-06-10 Honeywell International Inc. Vane radial mounting apparatus

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2222885A5 (de) * 1973-03-23 1974-10-18 Lucas Industries Ltd
JP3958484B2 (ja) * 2000-01-28 2007-08-15 株式会社荏原製作所 水中モータポンプ
CN2436703Y (zh) * 2000-04-27 2001-06-27 赖轩明 分压式离心泵
JP2002235689A (ja) * 2001-02-09 2002-08-23 Tsurumi Mfg Co Ltd ブースタポンプおよびその使用方法
DE20201183U1 (de) * 2002-01-25 2002-07-04 Allweiler Ag, 78315 Radolfzell Pumpe mit einen Antriebsmotor durchsetzender Pumpenwelle
JP4432474B2 (ja) * 2003-11-27 2010-03-17 ダイキン工業株式会社 遠心送風機の羽根車及びそれを備えた遠心送風機

Patent Citations (23)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1949796A (en) * 1931-08-29 1934-03-06 Himmelwerk Ag Pump or impeller
US2824520A (en) * 1952-11-10 1958-02-25 Henning G Bartels Device for increasing the pressure or the speed of a fluid flowing within a pipe-line
US2855141A (en) * 1955-11-25 1958-10-07 Jacobus C Van Rijn Two-piece cantilever fan and motor
US2968249A (en) * 1958-09-04 1961-01-17 Borg Warner Axial flow apparatus
US3102679A (en) * 1962-01-15 1963-09-03 Loren Cook Company Centrifugal impeller units
US3135212A (en) * 1962-03-29 1964-06-02 Symington Wayne Corp Submersible pump
US3244106A (en) * 1963-09-30 1966-04-05 North American Aviation Inc High pressure pumping device
US3398694A (en) * 1966-08-11 1968-08-27 Marine Constr & Design Co Submersible pump device for net brailing
US3836291A (en) * 1971-11-29 1974-09-17 Bosch Gmbh Robert Pump-and-motor unit, particularly for supplying fuel
US3826595A (en) * 1973-03-07 1974-07-30 Lucas Industries Ltd Electrically driven pump
US4213745A (en) * 1978-09-11 1980-07-22 Roberts Samuel A Pump for central heating system
US5487644A (en) * 1987-02-13 1996-01-30 Ishigaki Mechanical Industry Co., Ltd Pump having a single or a plurality of helical blades
US5494418A (en) * 1992-04-14 1996-02-27 Ebara Corporation Pump casing made of sheet metal
US5350281A (en) * 1993-01-26 1994-09-27 Sundstrand Corporation Fan with secondary air passage for motor cooling
US5567133A (en) * 1993-07-16 1996-10-22 Ebara Corporation Canned motor and pump employing such canned motor
US5674056A (en) * 1993-12-28 1997-10-07 Ebara Corporation Motor pump assembly
US6056518A (en) * 1997-06-16 2000-05-02 Engineered Machined Products Fluid pump
US6175173B1 (en) * 1998-09-15 2001-01-16 Wilo Gmbh Tube pump
US6135098A (en) * 1998-10-06 2000-10-24 Engineered Machine Products, Inc. Flow-through controllable air charger
US20020106290A1 (en) * 2001-02-05 2002-08-08 Engineered Machined Products, Inc. Electronic fluid pump
US20030021683A1 (en) * 2001-03-14 2003-01-30 Capone Christopher D. Touch down of blood pump impellers
US20040013547A1 (en) * 2002-07-17 2004-01-22 Engineered Machined Products, Inc. Electronic fluid pump
US20040109762A1 (en) * 2002-12-10 2004-06-10 Honeywell International Inc. Vane radial mounting apparatus

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20050248081A1 (en) * 2004-05-05 2005-11-10 Heidelberger Druckmaschinen Aktiengesellschaft Configuration for the transport and simultaneous alignment of sheets
US20130028760A1 (en) * 2011-07-29 2013-01-31 Lin Chih M Pump motor combination
US9261096B2 (en) * 2011-07-29 2016-02-16 Regal Beloit America, Inc. Pump motor combination
US20160201623A1 (en) * 2013-09-17 2016-07-14 Denso Corporation Liquid pump
US10148150B2 (en) * 2013-09-17 2018-12-04 Denso Corporation Liquid pump

Also Published As

Publication number Publication date
CN101365884A (zh) 2009-02-11
EP1945955A1 (de) 2008-07-23
WO2007054171A1 (de) 2007-05-18
CN101365884B (zh) 2011-09-28
EP1945955B1 (de) 2010-03-10
DE502006006411D1 (de) 2010-04-22
DE102005054027A1 (de) 2007-05-16
ATE460587T1 (de) 2010-03-15
JP2009515086A (ja) 2009-04-09

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Legal Events

Date Code Title Description
AS Assignment

Owner name: PIERBURG GMBH, GERMANY

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:GENSTER, ALBERT;REEL/FRAME:021565/0446

Effective date: 20080703

STCB Information on status: application discontinuation

Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION