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EP1945955B1 - Pompe a fluide - Google Patents

Pompe a fluide Download PDF

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Publication number
EP1945955B1
EP1945955B1 EP06806140A EP06806140A EP1945955B1 EP 1945955 B1 EP1945955 B1 EP 1945955B1 EP 06806140 A EP06806140 A EP 06806140A EP 06806140 A EP06806140 A EP 06806140A EP 1945955 B1 EP1945955 B1 EP 1945955B1
Authority
EP
European Patent Office
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.)
Not-in-force
Application number
EP06806140A
Other languages
German (de)
English (en)
Other versions
EP1945955A1 (fr
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
Publication of EP1945955A1 publication Critical patent/EP1945955A1/fr
Application granted granted Critical
Publication of EP1945955B1 publication Critical patent/EP1945955B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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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 relates to a fluid pump for internal combustion engines with an electric motor having a rotor disposed in a motor housing and a stator, wherein the rotor is at least rotationally fixed on a drive shaft, an impeller which is mounted on the drive shaft, at least one stator, which in Flow direction of the fluid to be conveyed is arranged behind the impeller, and a pump housing, which surrounds the motor housing, the impeller and the stator and on which opposite to the axial ends of a discharge nozzle and a suction nozzle are formed.
  • Fluid pumps for internal combustion engines are used in particular as coolant pumps in the cooling circuit. Whereas in the past there was a direct coupling to the engine speed and the pumps were driven by belt drives or chain drives, in newer engines variable speed electric coolant pumps with split tubes are increasingly used to realize a modern heat management. An abundance in the flow rate can thus be prevented, so that, for example, a faster heating of the internal combustion engine after the cold start is possible.
  • the flow rate can be regulated according to the actually required cooling capacity.
  • Such a pump is known for example from MTZ no.11 Jg.2005 (S. 872-877).
  • This electric coolant pump comprises an EC motor as a drive unit and has a pump head with axial inlet and tangential outlet.
  • the components used here and in particular housing parts are relatively large for the power consumption of the pump, since a relatively large drive motor must be used.
  • an electric fluid pump is disclosed in Halbaxialbauweise, with the same power consumption of the electric motor, this can be made smaller to achieve higher speeds, so that with smaller size equal flow rates can be achieved. It has a completely encapsulated electric motor, on whose outer side a stator is formed. In the flow direction behind the stator, however, obstacles to carry out the electrical contact with the electronics unit arise. On the impeller side, the entire motor is sealed by seals against the environment. To what extent such a seal on the rotating parts is sufficient at least questionable.
  • the pump housing is made in two parts and has different gradations and through holes for the electrical contact. Depending on the desired maximum flow rate different electric motors and housings have to be designed.
  • the DE 202 01 183 U1 which is considered to be the closest prior art, discloses an axial pump with an electric motor, which is surrounded by a housing part with straight support ribs, which are to serve as a stator. Due to its straight design, the pressure loss is very high. In addition, a swirl freedom is unlikely to be achieved by such an embodiment.
  • a pressure-side motor housing part has a Nachleitapparat, which is formed by return vanes.
  • This Nachleitapparat almost complete freedom from twist can be achieved, so that the kinetic energy of the tangential component of the flow velocity is converted with little friction losses in pressure energy. This increases the efficiency of the fluid pump. To achieve an equal flow rate, the size of the electric motor can thus be reduced.
  • the return vanes are made in one piece with the pressure-side motor housing part and formed on its surface, whereby no additional components are needed and the freedom from twist is ensured with low energy losses.
  • the return vanes serve to convert the tangential flow component into an axial flow component without higher pressure drops. The efficiency is increased and components saved.
  • the pressure-side motor housing part is narrowing in the flow direction and surrounded by a correspondingly shaped pressure-side pump housing part.
  • the return vanes are limited at their radial ends by the pump housing, so that an overflow of the blades is reliably prevented.
  • grooves are formed in the pressure-side pump housing part into which the radial ends of the return vanes extend. This in turn reduces the flow resistance by preventing overflow of the blades and fixes the position of the motor housing part to the pump housing part, so again mounting errors are avoided, since the grooves serve as guide grooves during assembly.
  • the pressure-side motor housing part by sliding the pressure-side pump housing part on the pressure-side motor housing part with the interposition of a seal in a receiving opening of an axially adjacent motor housing part displaceable, wherein fastening the pressure-side pump housing part to a axially adjacent motor housing part radially outboard pump housing part, the pressure-side motor housing part is fixed. Fasteners must not be used accordingly for the attachment of the pressure-side motor housing part. Alone by the attachment of the pump housing, a tight attachment of the motor housing is guaranteed, so that the assembly cost decreases.
  • the pressure-side pump housing part has a flange, via which the fluid pump can be fastened to an internal combustion engine. It is produced by the simplicity of the pump housing parts of the discharge nozzle in one piece with the flange, so that the fluid pump can be flanged without additional intermediate lines idrekt, for example, to a motor housing.
  • the figure shows a side view of a fluid pump according to the invention in a sectional view.
  • the fluid pump shown in the figure which is particularly suitable as a coolant pump in internal combustion engines, is driven by an electronically commutated electric motor 1, which consists of a stator 2 and a arranged on a drive shaft 3 rotor 4.
  • an impeller 5 is arranged, which is designed in a semi-axial design and by the rotation of the fluid to be delivered, in particular a coolant from a suction nozzle 6 is conveyed substantially axially through the fluid pump to a discharge nozzle 7.
  • the electric motor 1 is arranged in a motor housing which consists of a first suction-side motor housing part 8 and a second pressure-side motor housing part 9.
  • a motor housing which consists of a first suction-side motor housing part 8 and a second pressure-side motor housing part 9.
  • the suction-side motor housing part 8 Through the suction-side motor housing part 8, the drive shaft 3 is guided, on which the impeller 5 is arranged.
  • the suction-side motor housing 8 has a hole 10 in which a first bearing 11 is arranged for supporting the drive shaft 3.
  • the spacer serves to extend the distance of the first bearing 11 to a second bearing 15, whereby an angular error in the manufacture of the bore 10 for receiving the bearing can be better compensated.
  • a rotor laminated core 16 is arranged on the shaft, which has slits extending in the axial direction for receiving magnets 17, which correspond in a known manner with a stator winding 18.
  • the rotor 4 is bounded axially and radially by a capsule 19.
  • the stator winding 18 is wound on an insulating body 20 and delimits axially in a known manner a laminated stator core 21.
  • This laminated stator core 21 is connected in a form-fitting manner with a return plate 22 for closing the magnetic circuit.
  • This return plate 22 abuts against a stop 23, which is 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 split tube 24, which rests on the suction side of the pump in a corresponding receiving opening 25 of the suction-side motor housing part 8 and the opposite axial end is in turn arranged in a corresponding receiving opening 26 of the pressure-side motor housing part 9.
  • the stator 2 with its sensitive winding 18 thus lies in a separated by the two motor housing parts 8 and 9 and the can 24 dry space.
  • a closure member 27 is arranged, in which the second bearing 15 is arranged for mounting the drive shaft 3. Axially, this closure member 27 is secured by the pressure-side motor housing part 9, which is arranged with the interposition of a seal 28 in a receiving opening 29 of the suction-side motor housing part 8.
  • the support ribs 31 are shaped such that they also serve as a stator, so that no additional stator immediately behind the impeller 5 is necessary. This allows a simple one-piece production of the suction-side motor housing 8 with the support ribs and a cylindrical radially outer pump housing part 32. This pump housing part 32 surrounds the radially inner motor housing part 8 and the entire electric motor. 1
  • the suction side expanding in the flow direction pump housing part 33 comprises the suction nozzle 6 which is designed as a cylindrical portion 35 and an adjoining widening portion 36.
  • the suction nozzle 6 which is designed as a cylindrical portion 35 and an adjoining widening portion 36.
  • the semi-axial impeller 5 of the fluid pump is arranged in the transition region 37 between the first portion 35 and the second portion 36.
  • the expanding section 36 is followed by another short cylindrical section 38 of larger diameter, in order to achieve a clean transition to the cylindrical pump housing part 32.
  • grooves 39 are formed in the identical pump housing parts 33, 34, into which radial ends 40 of return vanes 41 engage.
  • These return blades 41 serve as a Nachleitapparat 42 by means of which behind the discharge nozzle 7 a completely twist-free flow is achieved.
  • This Nachleitapparat 42 is formed on a surface 43 of the pressure-side motor housing part 9 and is therefore necessary that the serving as a stator support ribs 31 are made relatively short and in this area of the fluid pump complete swirl reduction is not achieved in the rule.
  • the pressure-side motor housing part 9 can be produced in plastic, while the suction-side motor housing part is made as far as possible in aluminum and is therefore more expensive. An embodiment of the stator in this area would require a relatively expensive manufacturing process, while the Nachleitapparat the plastic housing part 9 is simple and inexpensive to manufacture.
  • the position of the pressure-side pump housing part 34 is set to the pressure-side motor housing part 9 at the same time.
  • the pressure-side pump housing part 34 via the return vanes 40, the motor housing part 9 against the motor housing part 8 and into the receiving openings 29 of the motor housing part 8. Furthermore, thereby the motor housing part 9 is pressed against the closure member 27 and the can 24, so that a additional attachment of the two motor housing parts 8, 9 is not necessary.
  • the fluid to be delivered in particular the coolant
  • the impeller 5 which consists of a plurality of impeller blades 44
  • a part of the fluid flows behind the impeller 5 through holes 45 which are formed in the suction-side motor housing part 8. Another part of the fluid also flows behind the impeller 5 to the drive shaft 3 and here between the first bearing 11 and the drive shaft 3, so that the existing sliding bearing is sufficiently lubricated.
  • coolant is in the rotor chamber, which in turn is continued between the drive shaft 3 and the second bearing 15 and by non-visible holes in the closure member 27 in a space 46 behind it.
  • This space 46 is connected via a further bore 47, which extends axially through the pressure-side motor housing part 9, with the space behind it.
  • This Halbaxialpumpe is characterized in particular by the fact that it is very small to build, since the same power consumption an equal capacity with a smaller motor size and increased speed compared to known To reach pumps. This is achieved in particular by the extremely reduced pressure losses in such a design, but also by the semi-axial design.
  • Such a pump can be produced very inexpensively, since there are fewer differently designed components. This simultaneously reduces possible errors during assembly. By eliminating the additional stator and the integration of the electrical contact in the support ribs additional components are avoided and reduces pressure losses. It is thus achieved a total of higher efficiency.
  • the suction-side pump housing part 33 it is also conceivable, by the simplicity, in particular of the suction-side pump housing part 33, to carry this integrally with valve housing parts, so that the pump housing part 33 has, for example, a receptacle for a bypass or an integrated thermostatic valve. Also, parts of the housing of a sliding ring valve could be made in one piece 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)

Claims (7)

  1. Pompe à fluide pour des moteurs à combustion interne, comprenant
    un moteur électrique avec un rotor et un stator disposé dans un boîtier de moteur, ledit rotor étant disposé sur un arbre d'entrainement au moins d'une manière à tourner avec ledit arbre,
    une couronne mobile montée sur ledit arbre d'entrainement,
    au moins une roue directrice située en aval de la couronne mobile, vu dans la direction d'écoulement du fluide à refouler,
    et un boîtier de pompe entourant ledit boîtier de moteur, la couronne mobile et la roue directrice et étant muni avec un raccord de refoulement et un raccord d'aspiration s'opposant à ses extrémités axiales,
    caractérisée en ce que
    une partie du boîtier de moteur (9) du côté de refoulement comprend un redresseur (42) formé par des pales de recirculation.
  2. Pompe à fluide pour des moteurs à combustion interne selon la revendication 1, caractérisée en ce que les pales de recirculation (41) sont réalisées d'un seul tenant avec ladite partie du boîtier de moteur (9) du côté de refoulement et sont formées sur sa surface (43).
  3. Pompe à fluide pour des moteurs à combustion interne selon la revendication 1 ou 2, caractérisée en ce que ladite partie du boîtier de moteur (9) du côté de refoulement est réalisée de sorte qu'elle s'effile dans la direction d'écoulement et est entourée par une partie du boîtier de pompe (34) du côté de refoulement ayant une forme correspondante.
  4. Pompe à fluide pour des moteurs à combustion interne selon l'une quelconque des revendications précédentes, caractérisée en ce que ladite partie du boîtier de pompe (34) du côté de refoulement est formée avec des rainures (39) dans lesquelles s'étendent les extrémités radiales (40) des pales de recirculation (41).
  5. Pompe à fluide pour des moteurs à combustion interne selon la revendication 4, caractérisée en ce que ladite partie du boîtier de moteur (9) du côté de refoulement est déplaçable, avec interposition d'un joint (28), dans une ouverture de logement (29) d'une partie du boîtier de moteur (8) axialement adjacente en poussant ladite partie du boîtier de pompe (34) du côté de refoulement sur ladite partie du boîtier de moteur (9) du côté de refoulement, ladite partie du boîtier de moteur (9) du côté de refoulement étant fixée par montage de ladite partie du boîtier de pompe (34) du côté de refoulement sur une partie du boîtier de pompe (32) située radialement à l'extérieure de ladite partie du boîtier de moteur (8) axialement adjacente.
  6. Pompe à fluide pour des moteurs à combustion interne selon l'une quelconque des revendications précédentes, caractérisée en ce que ladite partie du boîtier de pompe (34) du côté de refoulement présente une bride par lequel la pompe à fluide peut être montée sur un moteur à combustion interne.
  7. Pompe à fluide pour des moteurs à combustion interne selon l'une quelconque des revendications 1 à 5, caractérisée en ce que plusieurs pompes à fluide sont connectées en série par un joint à brides, les brides étant formées à ladite partie du boîtier de pompe (34) du côté de refoulement de la première pompe et à une partie du boîtier de pompe (33) du côté d'aspiration d'une pompe connectée en aval.
EP06806140A 2005-11-10 2006-10-10 Pompe a fluide Not-in-force EP1945955B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102005054027A DE102005054027A1 (de) 2005-11-10 2005-11-10 Fluidpumpe
PCT/EP2006/009763 WO2007054171A1 (fr) 2005-11-10 2006-10-10 Pompe a fluide

Publications (2)

Publication Number Publication Date
EP1945955A1 EP1945955A1 (fr) 2008-07-23
EP1945955B1 true EP1945955B1 (fr) 2010-03-10

Family

ID=37663301

Family Applications (1)

Application Number Title Priority Date Filing Date
EP06806140A Not-in-force EP1945955B1 (fr) 2005-11-10 2006-10-10 Pompe a fluide

Country Status (7)

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

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102004022141A1 (de) * 2004-05-05 2005-11-24 Heidelberger Druckmaschinen Ag Vorrichtung zum Fördern und gleichzeitigen Ausrichten von Bogen
US9261096B2 (en) * 2011-07-29 2016-02-16 Regal Beloit America, Inc. Pump motor combination
JP5958442B2 (ja) * 2013-09-17 2016-08-02 株式会社デンソー 液体ポンプ
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

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Also Published As

Publication number Publication date
CN101365884A (zh) 2009-02-11
US20090155100A1 (en) 2009-06-18
EP1945955A1 (fr) 2008-07-23
WO2007054171A1 (fr) 2007-05-18
CN101365884B (zh) 2011-09-28
DE502006006411D1 (de) 2010-04-22
DE102005054027A1 (de) 2007-05-16
ATE460587T1 (de) 2010-03-15
JP2009515086A (ja) 2009-04-09

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