EP1977114B1 - Laufrad - Google Patents

Laufrad Download PDF

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Publication number
EP1977114B1
EP1977114B1 EP07702382A EP07702382A EP1977114B1 EP 1977114 B1 EP1977114 B1 EP 1977114B1 EP 07702382 A EP07702382 A EP 07702382A EP 07702382 A EP07702382 A EP 07702382A EP 1977114 B1 EP1977114 B1 EP 1977114B1
Authority
EP
European Patent Office
Prior art keywords
impeller
width
flow
closed
design
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
EP07702382A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP1977114A1 (de
Inventor
Günther Beez
Holger Conrad
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.)
Mahle International GmbH
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Mahle International GmbH
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Filing date
Publication date
Application filed by Mahle International GmbH filed Critical Mahle International GmbH
Publication of EP1977114A1 publication Critical patent/EP1977114A1/de
Application granted granted Critical
Publication of EP1977114B1 publication Critical patent/EP1977114B1/de
Active legal-status Critical Current
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    • 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
    • F04D29/18—Rotors
    • F04D29/22—Rotors specially for centrifugal pumps
    • F04D29/2205—Conventional flow pattern
    • F04D29/2216—Shape, geometry
    • 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
    • F04D29/18—Rotors
    • F04D29/22—Rotors specially for centrifugal pumps
    • F04D29/24—Vanes
    • F04D29/242—Geometry, shape

Definitions

  • the invention relates to closed impellers for centrifugal pumps for the promotion of homogeneous fluids, in particular for use in automotive cooling systems.
  • the channel width initially remains the same in the region of the flow inlet and then tapers toward the outlet of the flow.
  • the open impeller designs are usually made in one piece in the plastic injection molding process, for example, from a thermoplastic or a thermoset material.
  • the closed design of the wheels can be made of plastic.
  • closed wheels with one or two-dimensional curved blades but also with the help of split slides for example, be made in one piece as plastic injection molded parts.
  • closed impellers with spatially curved blades have closed impellers with two-dimensionally curved blades (eg with a rectangular flow channel cross section, as in FIG DE PS 195 747 presented) at the same capacity on a larger specific diameter, a poorer suction behavior and an increased cavitation hazard.
  • the applicant of the present invention was therefore in the DE 197 42 023 B4 proposed a novel design for closed high-speed wheels with spatially curved blades, which in addition to precisely defined blade shapes, a high blade surface quality, good concentricity properties, high reliability, minimized manufacturing and assembly costs and high efficiency is.
  • the mostly used in series production impeller material plastic allows not only a cost-effective production of the individual components and a relatively inexpensive achievable, high surface quality, low friction, high corrosion resistance to the pumped medium as well as a high resistance to cavitation phenomena.
  • the cavitation arises in the operating condition of the impeller in areas of low pressure level, i. at a pressure below the vapor pressure of the fluid being conveyed, the effects of cavitation, i. the implosion of the cavitation bubbles and the wear resulting from this implosion, however, the cavitation erosion always occurs only in the areas of elevated pressure, i. mostly after the wheel up.
  • the impeller in the flow direction "downstream" components and assemblies are the pump housing and / or by integrating the pump in the engine, the timing case cover, the cylinder crankcase, the cylinder head oa ..
  • the aluminum casting has a much poorer resistance to cavitation erosion, so that cavitation building up in areas with low pressure levels in the impeller leads to damage due to cavitation erosion on the components and assemblies made of cast aluminum downstream of the impeller, which then become longer Continuous operation can lead to a total failure of these components / assemblies.
  • the invention is therefore based on the object to overcome the aforementioned disadvantages of the prior art and to develop a novel design of closed impellers for centrifugal pumps for the promotion of homogeneous fluids, especially for use in coolant pumps, which allows both closed wheels with single curved Shovels, as well as closed wheels with spatially curved blades cost to manufacture, to minimize the effects of Kavitationsverschl foundedes on the impeller downstream components / assemblies, while improving the hydraulic efficiency and the suction behavior of the respective impeller design significantly.
  • this object is achieved by means of an impeller according to claim 1.
  • the width of the blade channel in the meridian section increases continuously from the flow entering the impeller to the flow outlet from the impeller such that the ratio of the outlet width (b2) to the inlet width (b1) is in the range between 1.01 and 1.2.
  • the solution according to the invention due to the inventive effect of the displacement of the range of cavitation erosion in the impeller inevitably the effects of Kavitationsverschl foundedes to the Impeller downstream components / assemblies reduced to a minimum, or completely avoided.
  • the exit width (b2) can be dimensioned in a skilled manner (for example, according to the "speed triangle").
  • the larger exit width can be compensated by other parameters such as, for example, a smaller exit angle, the blade thickness, etc.
  • All required by the user performance data such as delivery and flow rate can be considered according to the usual in the art calculation methods for dimensioning the respective impeller, so that achieved by means of these novel, inventively designed wheels reliably all requested by the user performance data and by means of the invention Solution can be exceeded.
  • the ratio of the outlet width (b2) to the inlet width (b1) should always be in the range between 1.01 and 1.2, since with increasing outlet width (b2) increased recirculations occur in the impeller, which then lead to a separation of the flow.
  • FIG. 1 is designed as a radial impeller with simply curved blades 3 impeller 1 is shown in plan view.
  • FIG. 2 now shows the side view of a radial impeller after FIG. 1 on average at AA according to the in the DE 197 42 023 B4 above-described "segmented construction" with the bottom 2, the blades 3, a ceiling 4 and the blade segments interconnecting clamping ring 5, and as usual in the art, a relation to the entrance width b1 significantly reduced exit width b2.
  • FIG. 3 is the side view of the radial impeller after FIG. 1 in section AA at the design according to the invention, in one piece, with the bottom 2, the blades 3 and the ceiling 4, wherein (contrary to the usual in the art sizing) the outlet width b2 according to the invention compared to the inlet width b1 is increased.
  • FIG. 4 is designed as a Francis paddle wheel with spatially curved blades 3 impeller 1 is shown in plan view.
  • FIG. 5 now shows the side view of a Francis paddle wheel FIG. 4 on average at BB according to the in the DE 197 42 023 B4 above-described "segmented construction" with the bottom 2, the blades 3, a ceiling 4 and the blade segments interconnecting clamping ring 5, and as usual in the art, a relation to the entrance width b1 significantly reduced exit width b2.
  • FIG. 6 is the side view of the Francis Schaufelrades after FIG. 4 in section at BB according to the inventive design, in one piece, with the bottom 2, the blades 3 and the ceiling 4, wherein (contrary to the usual in the art sizing) the outlet width b2 according to the invention is increased compared to the inlet width b1.
  • FIG. 7 is a designed as a diagonal vane with spatially curved blades 3 impeller 1 is shown in plan view.
  • FIG. 8 now shows the side view of a Diagonalschaufelrades FIG. 7 on average at CC according to the in the DE 197 42 023 B4 above-described "segmented construction" with the bottom 2, the blades 3, a ceiling 4 and the blade segments interconnecting clamping ring 5, and as usual in the art, a relation to the entrance width b1 significantly reduced exit width b2
  • FIG. 9 is the side view of the diagonal paddle wheel FIG. 7 in section at CC according to the inventive design, in one piece, with the bottom 2, the blades 3 and the ceiling 4, wherein (contrary to the usual in the art sizing) the outlet width b2 according to the invention compared to the inlet width b1 is increased.
EP07702382A 2006-01-26 2007-01-20 Laufrad Active EP1977114B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102006003727A DE102006003727A1 (de) 2006-01-26 2006-01-26 Laufrad
PCT/DE2007/000104 WO2007085231A1 (de) 2006-01-26 2007-01-20 Laufrad

Publications (2)

Publication Number Publication Date
EP1977114A1 EP1977114A1 (de) 2008-10-08
EP1977114B1 true EP1977114B1 (de) 2010-06-16

Family

ID=37890748

Family Applications (1)

Application Number Title Priority Date Filing Date
EP07702382A Active EP1977114B1 (de) 2006-01-26 2007-01-20 Laufrad

Country Status (6)

Country Link
US (1) US8469671B2 (ja)
EP (1) EP1977114B1 (ja)
JP (1) JP4927097B2 (ja)
AT (1) ATE471458T1 (ja)
DE (3) DE102006003727A1 (ja)
WO (1) WO2007085231A1 (ja)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2652284A1 (de) * 2010-12-16 2013-10-23 Mahle International GmbH Sammelbehälter

Families Citing this family (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
RU2333397C2 (ru) * 2006-08-02 2008-09-10 Шлюмбергер Текнолоджи Б.В. Ступень погружного центробежного насоса
US8550039B2 (en) * 2010-10-28 2013-10-08 GM Global Technology Operations LLC Pump assembly and method of manufacturing same
SE536929C2 (sv) * 2011-05-09 2014-11-04 Luossavaara Kiirunavaara Ab Rotormaskin avsedd att arbeta som pump eller omrörare samt en impeller för en sådan rotormaskin
US9309895B2 (en) 2012-06-18 2016-04-12 Kennametal Inc. Closed impeller with a coated vane
CN103452900B (zh) * 2013-09-18 2015-06-10 成都市永益泵业有限公司 一种可提高泵效率的离心叶轮几何参数优化设计方法
DE102014201487B3 (de) * 2014-01-28 2015-03-05 Bühler Motor GmbH Kreiselpumpenlaufrad
WO2016117709A1 (en) * 2015-01-19 2016-07-28 Ebara Corporation Centrifugal impeller for fluid-operated pumps, and method for manufacturing the impeller
ITUB20150308A1 (it) * 2015-05-04 2016-11-04 Ebara Corp Struttura di girante, particolarmente per pompe centrifughe
CN106949088A (zh) * 2017-05-20 2017-07-14 江苏斯别特制泵有限公司 一种特殊改进的大功率潜水混流泵叶轮
CN107747562A (zh) * 2017-10-27 2018-03-02 珠海格力电器股份有限公司 混流风轮的叶片组件、混流风轮及具有混流风轮的装置
RU187738U1 (ru) * 2018-05-25 2019-03-15 Общество с ограниченной ответственностью "Ижнефтепласт" Рабочее колесо центробежного насоса
KR102234649B1 (ko) * 2019-04-29 2021-03-31 강원대학교산학협력단 밀폐형 원심펌프 임펠러
CN111396351A (zh) * 2020-04-27 2020-07-10 西安航空学院 一种扩口增压的超低比转速离心泵叶轮

Family Cites Families (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE195747C (de) * 1905-12-10 1908-02-24 Neumann Fritz Laufräder von zentrifugalpumpen, bei denen die schaufeln gekrümmt sind und die eintrittshöhe grösser als die austrittshöhe ist
CH269595A (de) * 1946-12-20 1950-07-15 Egger Emile Zentrifugalpumpe.
DE843812C (de) * 1947-10-25 1952-07-14 Sulzer Ag Kreiselpumpe fuer nicht homogene Foerderstoffe
DE897801C (de) * 1949-09-04 1953-11-23 Pleuger Kommanditgesellschaft Laufrad fuer Kreiselpumpen
DE1176485B (de) * 1958-01-31 1964-08-20 Eta Corp G M B H Kreiselradmaschine, insbesondere Kreiselrad-pumpe, mit im Meridianschnitt sich erweiterndem Stroemungsweg
US3775024A (en) * 1970-05-20 1973-11-27 Airtex Prod Division Of United Submersible fuel pump
US4253798A (en) * 1978-08-08 1981-03-03 Eiichi Sugiura Centrifugal pump
US4666373A (en) * 1986-03-20 1987-05-19 Eiichi Sugiura Impeller for rotary fluid machine
JPS6360095A (ja) * 1986-08-29 1988-03-16 Tokushu Denkyoku Kk 硬化肉盛金属
DE3632259C2 (de) * 1986-09-23 1995-11-23 Eaton Gmbh Verfahren zur Herstellung eines Pumpenlaufrades für eine Kühlmittelpumpe in einem Kraftfahrzeug
AUPN715595A0 (en) 1995-12-14 1996-01-18 Warman International Limited Improved centrifugal pump
JP4016441B2 (ja) * 1996-10-02 2007-12-05 株式会社ジェイ・エム・エス ターボ式血液ポンプ
DE19742023B4 (de) 1997-09-24 2006-07-13 Beez, Günther, Dipl.-Ing. Laufrad
US6413039B1 (en) * 2000-06-01 2002-07-02 Uis, Inc Impeller for coolant pumps

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2652284A1 (de) * 2010-12-16 2013-10-23 Mahle International GmbH Sammelbehälter

Also Published As

Publication number Publication date
ATE471458T1 (de) 2010-07-15
EP1977114A1 (de) 2008-10-08
DE112007000708A5 (de) 2008-12-24
DE502007004127D1 (de) 2010-07-29
US20090016895A1 (en) 2009-01-15
US8469671B2 (en) 2013-06-25
JP4927097B2 (ja) 2012-05-09
JP2009524759A (ja) 2009-07-02
WO2007085231A1 (de) 2007-08-02
DE102006003727A1 (de) 2007-08-02

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