EP2708754A2 - Pompe - Google Patents

Pompe Download PDF

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Publication number
EP2708754A2
EP2708754A2 EP13182883.2A EP13182883A EP2708754A2 EP 2708754 A2 EP2708754 A2 EP 2708754A2 EP 13182883 A EP13182883 A EP 13182883A EP 2708754 A2 EP2708754 A2 EP 2708754A2
Authority
EP
European Patent Office
Prior art keywords
impeller
bearing
pump
rotor
inlet
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP13182883.2A
Other languages
German (de)
English (en)
Other versions
EP2708754A3 (fr
Inventor
Uwe Kögel
Stefanie Roth
Tobias Albert
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.)
EGO Elektro Geratebau GmbH
Original Assignee
EGO Elektro Geratebau 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 EGO Elektro Geratebau GmbH filed Critical EGO Elektro Geratebau GmbH
Publication of EP2708754A2 publication Critical patent/EP2708754A2/fr
Publication of EP2708754A3 publication Critical patent/EP2708754A3/fr
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/04—Shafts or bearings, or assemblies thereof
    • F04D29/046—Bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/04—Shafts or bearings, or assemblies thereof
    • F04D29/041—Axial thrust balancing
    • F04D29/0413—Axial thrust balancing hydrostatic; hydrodynamic thrust bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/04—Shafts or bearings, or assemblies thereof
    • F04D29/046—Bearings
    • F04D29/0467—Spherical bearings
    • 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
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/426—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for liquid pumps
    • F04D29/4293—Details of fluid inlet or outlet

Definitions

  • the invention relates to a pump according to the preamble of claim 1.
  • the invention has for its object to provide an aforementioned pump, can be avoided with the disadvantages of the prior art and in particular a practical axial support of the impeller is possible with simple production.
  • the pump has a pump chamber and a rotor or impeller rotating therein.
  • Into the pump chamber in a pump housing introduces an inlet and an outlet leads out again.
  • the pump has a pump motor with a rotor, wherein rotor and impeller are interconnected.
  • the pump motor is brushless.
  • the impeller which is usually pulled towards the inlet during operation, is supported in this axial direction towards the inlet or away from the rotor, for which purpose an axial support against an axial bearing is provided.
  • the axial bearing is located on a rotation axis or axis of rotation of the rotor, ie in the center. This means that the axis of rotation of the rotor and thus also the impeller passes through a bearing surface of the thrust bearing. In this case, this axis of rotation of the rotor must not be confused with the motor axis, although of course the axis of rotation passes centrally through the motor axis.
  • Another advantage is that the arrangement of the impeller in the pump housing is much more precise possible while simplifying the manufacture of the pump. By bearing with the thrust bearing in the area where it is important for the impeller, it can be very precise. This will be explained in more detail below.
  • rotor and impeller are designed as a structural unit. They can not only be mounted together somehow, but advantageously be insoluble or made in one piece.
  • the formation of rotor and impeller as a unit is advantageously carried out before assembly of the pump.
  • rotor and impeller can be made as a unit in one piece in a plastic injection molding of plastic, particularly advantageous in two or three steps.
  • the assembly of rotor and impeller can be advantageously designed such that the impeller is, so to speak, placed directly on the rotor or at least no pump chamber wall is located therebetween.
  • no pump chamber floor should be in between, so that construction or assembly are very easy to perform.
  • the impeller advantageously has a larger diameter than the rotor, so that the structural unit can be mounted in the direction of the engine.
  • the thrust bearing is in extension of the inlet, in the region or within the inlet. It can thereby be achieved that the basic design of the impeller does not have to be changed very much by the thrust bearing according to the invention.
  • the inlet of one of the parts of the pump housing which are closest to the impeller in the region of the rotational axis of the rotor is particularly advantageous.
  • Such is the arrangement of the Axial bearings relatively easy.
  • thrust bearing also disturbs the inflow of the pumped fluid into the pump into little, since such impeller pumps are usually pressure pumps and no suction pumps.
  • the arrangement of the thrust bearing on the axis of rotation of the rotor centrally in the inlet of advantage which advantageously also extends coaxially to this axis of rotation, whereby no large inflow resistance is formed.
  • the thrust bearing can be seen radially within the impeller or at its axial height, in particular in its upper end region. So just the structure of the impeller can be largely conventional.
  • the thrust bearing is substantially free in the inlet or is arranged there. It is supported by means of several supports at the inlet, in particular in the manner of struts, which are particularly preferably in the radial direction and may be formed flat in cross-section such that they just form the lowest possible flow resistance in the axial direction.
  • the impeller may have a tubular top facing towards the inlet.
  • the inlet in particular an aforementioned elongated inlet, may comprise or form a collar which overlaps the tubular upper part of the impeller and which likewise has approximately the shape of a short tube.
  • This collar can in particular form a taper of the inlet.
  • the tubular upper part and the collar overlap each other in the axial direction, which serves to avoid too large aforementioned backflow of water from the pressure side to the suction side.
  • the collar a piece extend into the tubular upper part of the impeller.
  • the supports provided for the axial bearing extend at the end of this collar or as far as possible in the direction of the impeller and can thus be arranged within the tubular upper part of the impeller.
  • the thrust bearing extends quasi as far as possible to the impeller.
  • the plain bearing may have a bearing surface.
  • Slide bearing and bearing projection can be designed such that they have a curvature and indentation, which are applied against each other or to each other and rotate together. Due to the shape of the curvature and indentation can advantageously be achieved that a centering of the assembly or the impeller is carried on the axis of rotation of the rotor and thus also the entire pump.
  • Buckle and indentation are advantageously designed such that the indentation has a larger radius or is less curved than the curvature that lies in it.
  • the slide bearing on the thrust bearing concave curved form away from the impeller and the bearing projection on the impeller with a convex curvature away from this.
  • a tip or curvature of the bearing projection of the impeller in the recess or indentation of the thrust bearing at the inlet of the pump housing.
  • Preference is given to an approximately uniform or rounded curvature.
  • the tip on the thrust bearing could actually be provided a very fine tip. Then, however, a point-shaped storage would essentially result, which in turn is susceptible to wear and also makes very high demands on a production.
  • the axial bearing made of plastic.
  • the other part may also be made of plastic, alternatively made of metal or graphite or ceramic.
  • At least one inwardly curved slide bearing as a recess should be made of plastic.
  • generally preferred plastics can be used for such bearings, for example polyamide, Teflon-reinforced, POM or generally fiber-reinforced plastics. Sinterbronze or brass are suitable as metallic materials, in particular because of their corrosion resistance when using the pump in a dishwasher.
  • a sliding bearing of the axial bearing on the pump housing or in the inlet is advantageously injected or injected. Thus, it can be attached thereto in the same operation of manufacturing the pump housing.
  • a bearing on the plain bearing of the thrust bearing bearing projection of the impeller is advantageously also molded or injected at this. Again, there are the benefits of simple and accurate manufacturing. Alternatively, it could also be a usable from above separate part, which in any case can not fall out of the impeller by the system pressure on the thrust bearing during operation of the pump.
  • the assembly rotates on a fixed motor axis, which runs coaxially with the axis of rotation of the rotor.
  • This motor shaft may be fixed to the end facing away from the impeller, in particular to a motor housing at the end facing away from the inlet end of the pump.
  • it is a round motor shaft which rotates in a bearing bush, which is arranged in the rotor, in particular injected.
  • the length of the motor shaft can be freely selected within wide limits. It can be almost as long as the entire assembly of rotor and impeller.
  • the motor axis does not need to be very long and can protrude only a few inches or only a small piece into the rotor. Essentially, this short motor axis must then ensure a radial securing or centering of the rotor or the structural unit.
  • the centering at the other end of the assembly is formed by the thrust bearing at the inlet, which is sufficient overall.
  • a pump 11 according to the invention is shown in a sectional side view. It has a pump part 12 with a pump chamber 13 in a pump housing 14.
  • the pump 11 is obviously designed as an impeller pump and can be advantageously used in a water-conducting household appliance, in particular a dishwasher or a washing machine.
  • a central inlet 16 leads along a dash-dotted longitudinal center axis.
  • the inlet 16 has an inlet tube 17, which opens into a radially inner collar 18.
  • an outlet 19 is provided on the pump housing 14, see also the plan view Fig. 3 ,
  • the pump 11 has a motor part 20 with a stator 21 and a rotor 22, which has a rotor laminated core 23 and magnets 23 '. It is therefore a brushless wet rotor, as it is known and familiar for such applications.
  • the impeller 30 adjoins the region of the rotor 22 surrounding the rotor laminated core 23 and the magnets 23 'or is produced in one piece therewith, in particular by an aforementioned plastic injection molding.
  • the impeller 30 has a bottom disk 31 and a cover disk 32 with therebetween arranged, curved impeller blades 33.
  • Such impellers are known in the art, see for example the DE 102012209832.1 the same applicant with filing date of June 12, 2012.
  • the central axis 35 raises a central projection 35 on the bottom plate 31.
  • the motor shaft 26 may extend into this central projection 35 into it, but need not be so long and can, for example, extend only to the lower end of the bearing bush 25.
  • a bearing projection 37 is provided or arranged, which is slightly convexly curved or toward the inlet 16. This is from the following explained strong magnification in Fig. 2 clear.
  • a bearing 39 according to the invention is shown here, for the sake of clarity in a state in which no contact has yet been reached. So there is still a small distance, which may correspond, for example, a resting state of the pump 11.
  • the thrust bearing 39 on a bearing shell 40, which is arranged in a bearing holder 41, for example, pressed or injected. It may also be the same part.
  • the bearing holder 41 in turn is about three struts 42, the radial arrangement of Fig. 3 can be seen on the pump housing 14 and held on the inlet tube 17 and collar 18.
  • the thrust bearing 39 and bearing holder 41 and strut 42 may advantageously be formed integrally with the inlet.
  • the pump 11 When the pump 11 starts, it pulls the impeller 30 toward the inlet 14, in the Fig. 1 So down. As a result, the bearing projection 37 comes to rest on the bearing shell 40 of the axial bearing 30.
  • the outwardly arched bearing projection 37 with a smaller radius or one The difference may, for example, be given geometrically such that the radius, in the case of circular areas or approximate circular areas, of the bearing shell 40 is 1.5 times to 4 times larger as the one of the bearing projection 37.
  • the bearing projection 37 may consist of the same plastic as the other impeller 30. Alternatively, it may consist of a separate applied material. The same applies to the bearing shell 40, for this reference is made to the examples described above for respective material choices.
  • a modification of a thrust bearing 139 is shown.
  • the principle of the arrangement of the thrust bearing 139 on the axis of rotation of the rotor is the same, also here three struts 142 are provided.
  • the bearing holder 141 is here, however, not curved inward as in Fig. 2 but arched outwards or forms the bulged part of the thrust bearing 139th
  • Adjacent to the bearing projection 137 of the impeller 130 has a recess shell 138 as quasi bearing shell. This can, as indicated, made of a different material than the bearing projection 137 and be molded or attached. Similar to already in Fig. 2 are in the Fig. 4 the bulges formed differently strong for a good ratio of abutting surface and centering effect.
  • Fig. 5 is a still further modification shown, the one from the Fig. 2 similar.
  • the thrust bearing 239 here has a bearing shell 240 which is held by three struts 242.
  • the bearing shell 240 is supported by a bearing holder 241 and is advantageously made of hard material or metal, in particular brass.
  • a bearing tip 244 is provided, which advantageously also consists of metal and is attached or molded. While the bearing cup 240 is substantially curved, similar to the previous embodiments, the bearing tip 244 is much sharpened. It can either be formed directly as a tip as fine as possible, alternatively also have a flattening of about 1 mm in diameter at the front or a corresponding rounding.
  • Another great advantage of the design of the pump 11 with a thrust bearing 39 is that the axial position of the impeller 30 in the pump chamber 13 can be accurately determined.
  • a gap between the impeller 30 or cover disk 32 and the tubular upper part 34 towards the pump housing 14, in particular in the region of the inlet pipe 17 or the collar 18, can be minimized without running the risk of a direct concern.
  • a loss flow typical of impeller pumps can be reduced from the pressure side to the suction side.
  • the efficiency or energy efficiency of the pump 11 is increased.
  • This very precise storage is favored in addition to the axial support by the centering due to the special design of the thrust bearing 39.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
EP13182883.2A 2012-09-12 2013-09-03 Pompe Withdrawn EP2708754A3 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102012216196.1A DE102012216196A1 (de) 2012-09-12 2012-09-12 Pumpe

Publications (2)

Publication Number Publication Date
EP2708754A2 true EP2708754A2 (fr) 2014-03-19
EP2708754A3 EP2708754A3 (fr) 2015-01-07

Family

ID=49123701

Family Applications (1)

Application Number Title Priority Date Filing Date
EP13182883.2A Withdrawn EP2708754A3 (fr) 2012-09-12 2013-09-03 Pompe

Country Status (4)

Country Link
US (1) US20140072414A1 (fr)
EP (1) EP2708754A3 (fr)
CN (1) CN103671131A (fr)
DE (1) DE102012216196A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3293304A1 (fr) * 2016-09-13 2018-03-14 Lg Electronics Inc. Pompe de drainage

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102013211181B3 (de) 2013-06-14 2014-08-21 E.G.O. Elektro-Gerätebau GmbH Pumpe
DE102017203736A1 (de) 2017-03-07 2018-09-13 Mahle International Gmbh Elektromotor
DE102017203833A1 (de) * 2017-03-08 2018-09-13 Mahle International Gmbh Flüssigkeitspumpe
IT201700045437A1 (it) * 2017-04-27 2018-10-27 Ind Saleri Italo Spa Gruppo pompa con elemento di fissaggio
JP7181443B2 (ja) * 2018-02-14 2022-12-01 日本電産サンキョー株式会社 冷却装置
DE102019115774A1 (de) * 2019-06-11 2020-12-17 HELLA GmbH & Co. KGaA Pumpe, insbesondere Pumpe für einen Flüssigkeitskreislauf in einem Fahrzeug, mit einem Kranz eines Laufrades, eintauchend in ein Gehäuse
WO2021218728A1 (fr) * 2020-04-30 2021-11-04 杭州三花研究院有限公司 Procédé de fabrication d'un ensemble rotor, ensemble rotor et pompe électrique
DE102020121332B4 (de) * 2020-08-13 2024-10-24 Nidec Gpm Gmbh Axialgleitlageranordnung für eine zu lagernde Welle eines Pumpenrads einer Radialpumpe sowie Radialpumpe aufweisend die Axialgleitlageranordnung
DE102021205247A1 (de) * 2021-05-21 2022-11-24 E.G.O. Elektro-Gerätebau GmbH Pumpe für ein wasserführendes Haushaltsgerät und wasserführendes Haushaltsgerät mit einer solchen Pumpe

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19921365B4 (de) 1999-05-10 2010-07-29 Pierburg Gmbh Elektromagnetisch betriebene Pumpe mit Axialspaltlager

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US4730989A (en) * 1984-10-11 1988-03-15 Karsten Laing Rotodynamic pump with spherical bearing
US4722661A (en) * 1985-10-09 1988-02-02 Ngk Insulators, Ltd. Magnetic-drive centrifugal pump
US5713730A (en) * 1992-09-04 1998-02-03 Kyocera Corporation Ceramic pivot bearing arrangement for a sealless blood pump
IL109967A (en) * 1993-06-15 1997-07-13 Multistack Int Ltd Compressor
JPH08182243A (ja) * 1994-12-22 1996-07-12 Nippondenso Co Ltd モータおよびそれを用いた燃料ポンプ
JP2000337292A (ja) * 1999-05-24 2000-12-05 Matsushita Electric Ind Co Ltd ポンプ
JP2001329989A (ja) * 2000-05-22 2001-11-30 Matsushita Electric Ind Co Ltd ターボ型ポンプ
DE10140613A1 (de) * 2001-08-18 2003-03-06 Pierburg Gmbh Naßläuferpumpe
DE10222252A1 (de) * 2002-05-16 2003-11-27 Siemens Ag Fördereinheit
DE10352487A1 (de) * 2003-07-22 2005-02-10 BSH Bosch und Siemens Hausgeräte GmbH Pumpe mit integriertem Motor
JP5130052B2 (ja) * 2005-11-29 2013-01-30 京セラメディカル株式会社 血液ポンプ
JP2007211679A (ja) * 2006-02-09 2007-08-23 Mitsubishi Electric Corp 円周流ポンプ
JP4274230B2 (ja) * 2006-11-21 2009-06-03 パナソニック電工株式会社 ポンプ
DE102007043600A1 (de) * 2007-09-13 2009-03-19 Robert Bosch Gmbh Pumpenrotor für eine Spaltrohrpumpe
JP5058896B2 (ja) * 2008-06-26 2012-10-24 日立オートモティブシステムズ株式会社 電動遠心ポンプ
CN102667167A (zh) * 2010-02-02 2012-09-12 三菱重工业株式会社 离心泵
DE102011005138A1 (de) * 2011-03-04 2012-09-06 E.G.O. Elektro-Gerätebau GmbH Pumpe
DE102012209832B3 (de) 2012-06-12 2013-09-12 E.G.O. Elektro-Gerätebau GmbH Pumpe und Verfahren zum Herstellen eines Impellers für eine Pumpe

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19921365B4 (de) 1999-05-10 2010-07-29 Pierburg Gmbh Elektromagnetisch betriebene Pumpe mit Axialspaltlager

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3293304A1 (fr) * 2016-09-13 2018-03-14 Lg Electronics Inc. Pompe de drainage
US10793992B2 (en) 2016-09-13 2020-10-06 Lg Electronics Inc. Drain pump

Also Published As

Publication number Publication date
DE102012216196A1 (de) 2014-03-13
CN103671131A (zh) 2014-03-26
EP2708754A3 (fr) 2015-01-07
US20140072414A1 (en) 2014-03-13

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