EP2699803B1 - Laufrad für kreiselpumpen - Google Patents

Laufrad für kreiselpumpen Download PDF

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Publication number
EP2699803B1
EP2699803B1 EP12717260.9A EP12717260A EP2699803B1 EP 2699803 B1 EP2699803 B1 EP 2699803B1 EP 12717260 A EP12717260 A EP 12717260A EP 2699803 B1 EP2699803 B1 EP 2699803B1
Authority
EP
European Patent Office
Prior art keywords
blade
impeller
section
angle
impeller according
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
EP12717260.9A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP2699803A2 (de
Inventor
Peer Springer
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.)
KSB SE and Co KGaA
Original Assignee
KSB SE and Co KGaA
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 KSB SE and Co KGaA filed Critical KSB SE and Co KGaA
Publication of EP2699803A2 publication Critical patent/EP2699803A2/de
Application granted granted Critical
Publication of EP2699803B1 publication Critical patent/EP2699803B1/de
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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
    • F04D29/18—Rotors
    • F04D29/22—Rotors specially for centrifugal pumps
    • F04D29/24—Vanes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D5/00—Blades; Blade-carrying members; Heating, heat-insulating, cooling or antivibration means on the blades or the members
    • F01D5/12—Blades
    • F01D5/14—Form or construction
    • F01D5/141—Shape, i.e. outer, aerodynamic form
    • 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
    • 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
    • F04D29/2261—Rotors specially for centrifugal pumps with special measures
    • F04D29/2294—Rotors specially for centrifugal pumps with special measures for protection, e.g. against abrasion
    • 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 an impeller for centrifugal pumps with at least two blades for conveying media containing solids.
  • the DE 40 15 331 A1 describes an impeller with only one blade.
  • the bucket wheel produced by a casting process forms a channel between a front cover disk and a rear cover disk and a bucket, the cross section of which decreases from the inlet of the bucket wheel to the outlet.
  • the suction side forms a semicircle arranged concentrically to the axis of rotation on the first 180 ° of the angle of rotation.
  • the impeller is designed to prevent premature blistering and thus cavitation.
  • the blade head has a very large radius of curvature. This flattening prevents long-fiber components from attaching.
  • impellers with several blades are characterized by a higher degree of efficiency.
  • impellers also have special requirements with regard to preventing solid components from accumulating in the conveying path.
  • special measures must be taken to avoid blockages.
  • the suitability of these impellers for wastewater is checked, among other things, with the ball passage.
  • the ball passage describes the ability of the impellers to convey large solid bodies corresponding to a ball.
  • Centrifugal pumps with high specific speeds are increasingly used in wastewater technology.
  • the leading edges of the blades are flowed around from the pressure side to the suction side.
  • the stagnation point on the pressure side presses the fibers in the wastewater firmly onto the surface of the blades.
  • the high-speed area is followed by an area with a lower speed.
  • Dead water is created there. Fibers adhering to the leading edge tend to fill this dead water. Due to the flow around the fibers are pressed onto the blade contour, whereby the assignment of fibers can increase significantly.
  • the object of the present invention is to provide an impeller with a high degree of efficiency, in which deposits and the occurrence of cavitation are avoided.
  • the blade entry angle is: less than 0 °, the blade angle increasing in a first section until it reaches one Value of 0 ° reached, then increases in a second section up to a maximum value and decreases in a third section.
  • the blade angle at the inlet is less than 0 ° and then increases. This leads to a strong curvature of the blade contour.
  • the angular course ensures an even load on the entire blade surface.
  • the stagnation point of the flow shifts from the pressure side to the area of maximum curvature of the leading edge or even to the suction side. This reduces the load on the blade leading edge and the forces that press the fibers in the entry area.
  • a high-speed area forms on the suction side of the blades, which contributes to detachment of adhering fibers. After reaching a maximum value, the blade angle drops again.
  • the blade course shows an S-stroke.
  • the goal of the interpretation is; to reduce the load on the blade leading edge and the pressure-side dynamic pressure area.
  • the course of the blade profile according to the invention and thus the blade angle also achieves a further flow acceleration in partial load operation in the partial load area, as a result of which the separation area is kept small.
  • the point of highest flow speed is thus placed in the middle part of the blade suction side.
  • the blade angle remains constant in a subsequent fourth section.
  • the impeller has a constantly small blade angle in the radial area of the pump. The expansion of the return flow area on the pressure side is reduced by loading the suction side. The small blade outlet angle reduces the load at the blade end and reduces the area of the backflow area on the blade pressure side.
  • the blade angle in the inlet area is less than -10 °.
  • the small entry angles lead to a hydraulically shock-free flow.
  • the blade angle increases until it reaches a value of 0 °. Then in a second section there is a further increase in the blade angle until a maximum value is reached.
  • the blade angle preferably increases with the same gradient in the first and second sections.
  • the blade angle increases in the first and / or second section with a gradient of more than 0.35.
  • the strong curvature leads to a homogeneous blade load in the middle area of the blade surface. Due to the extreme angle increase in the front part of the bucket, the load distribution is maintained even at partial load. The increased stress on the leading edge, which normally increases the adhesion effect, is thereby reduced.
  • the blade angle drops to the blade exit angle in a third section from a turning point.
  • the blade angle preferably remains constant.
  • the ratio of blade outlet radius to blade inlet radius is preferably less than 1.5. This enables the impeller to be operated effectively even at high specific speeds.
  • impellers With conventional impellers, large radii of curvature of the blade leading edges are required in order to avoid high flow rates and the associated occurrence of cavitation. This causes material accumulations that lead to heavy impellers. Because of the blade angle curve according to the invention, it is possible to use impellers; which have a small radius of curvature of the blade leading edges. The radius of curvature of the blade leading edges is preferably equal to or less than the value of the blade thickness in the fourth region. Despite the high flow velocities that occur, there is no cavitation damage to the impellers according to the invention. The impellers can be made slim and light due to the small radius of curvature of the blade leading edges.
  • the impeller used to convey waste water preferably comprises two or three blades. Such designs are particularly suitable for waste water with a high proportion of solid admixtures and are also referred to as two-channel or three-channel. If the number of blades is too large, there is a risk of blockage. Compared to single-bladed wheels, the two- or three-bladed impellers ensure a higher degree of efficiency and, due to the lack of unbalance and less pulsation, better operating behavior.
  • the impeller preferably has a cover disk and is therefore designed in a closed design.
  • Fig. 1 is an axial section through a radial impeller.
  • the liquid interspersed with solid admixtures enters the impeller through the suction mouth 1.
  • the blades 4 arranged between the cover disk 2 and the support disk 3 accelerate the liquid.
  • the liquid flows radially outward from the axis of rotation 5.
  • the impeller is operated at specific speeds of more than 70.
  • a low ratio of blade outlet radius R 2 to blade inlet radius R 1 proves to be particularly favorable. In the exemplary embodiment, the ratio of blade outlet radius R 2 to blade inlet radius R 1 is less than 1.3.
  • FIG. 2a and 2b is a front view and a perspective view of the blades 4 of the impeller.
  • the impeller comprises two blades 4 that are attached to a support disk 3.
  • the impeller rotates clockwise with a view of the representations.
  • the blade leading edges 6 have a small radius of curvature.
  • the radius of curvature is 7 mm in the exemplary embodiment.
  • the solids-containing medium is accelerated by the blades 4.
  • a distinction is made between the pressure side 7 and the suction side 8 of the blades 4.
  • Fig. 3a the course of the blade angle ⁇ is shown.
  • Fig. 3b shows a conformal image of the skeletal line.
  • the wrap angle ⁇ is plotted on the abscissa.
  • the blade angle ⁇ of the skeleton line is plotted on the ordinate.
  • the blade entry angle ⁇ 1 is less than 0 °.
  • the blade angle ⁇ increases steadily until it reaches a value of 0 °.
  • a second section 10 there is a further steady increase until the blade angle ⁇ reaches a maximum value.
  • the gradient of the increase in the blade angle ⁇ in the first section 9 and second section 10 are the same.
  • the blade angle ⁇ reaches its maximum value at the turning point of the skeleton line.
  • a third section 11 the blade angle ⁇ drops steadily until it reaches the value of the blade exit angle ⁇ .
  • the blade angle ⁇ remains constant at the value of the blade exit angle ⁇ 2 .
  • the conformal image of the skeleton line shows that, starting from the blade entry radius R 1, the radius initially drops to a minimum value R min and then continues to increase to the value of the blade exit radius R 2 .
  • FIGS. 4a and 4b show a radial section of a two-bladed vehicle showing the streamlines that have different speeds.
  • the impeller rotates counterclockwise with a view of the figures.
  • the stagnation point 13 of the flow is not on the pressure side 7 but in the area of maximum curvature of the blade leading edge 6.
  • an area 14 of high speeds is formed, which contributes to detachment: adhering fibers.
  • the load on the blade leading edge 6 is reduced. As a result, the forces which press fibers in the entry region decrease. Due to the load on the middle suction-side area of the blade 4, high speeds occur there, as a result of which adhering fibers are removed.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Geometry (AREA)
  • Fluid Mechanics (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
EP12717260.9A 2011-04-21 2012-04-18 Laufrad für kreiselpumpen Active EP2699803B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102011007907A DE102011007907B3 (de) 2011-04-21 2011-04-21 Laufrad für Kreiselpumpen
PCT/EP2012/057035 WO2012143367A2 (de) 2011-04-21 2012-04-18 Laufrad für kreiselpumpen

Publications (2)

Publication Number Publication Date
EP2699803A2 EP2699803A2 (de) 2014-02-26
EP2699803B1 true EP2699803B1 (de) 2020-04-29

Family

ID=46017835

Family Applications (1)

Application Number Title Priority Date Filing Date
EP12717260.9A Active EP2699803B1 (de) 2011-04-21 2012-04-18 Laufrad für kreiselpumpen

Country Status (15)

Country Link
US (1) US9556739B2 (ja)
EP (1) EP2699803B1 (ja)
JP (1) JP6092186B2 (ja)
KR (1) KR101868132B1 (ja)
CN (1) CN103534489B (ja)
AU (1) AU2012244804B2 (ja)
BR (1) BR112013026753A2 (ja)
CA (1) CA2833193C (ja)
DE (1) DE102011007907B3 (ja)
DK (1) DK2699803T3 (ja)
HU (1) HUE051436T2 (ja)
MX (1) MX2013010939A (ja)
RU (1) RU2580237C2 (ja)
WO (1) WO2012143367A2 (ja)
ZA (1) ZA201307151B (ja)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2888484B1 (de) * 2012-08-23 2021-02-17 Sulzer Management AG Pumpe zum fördern von abwasser sowie laufrad und bodenplatte für eine solche
CN103016398B (zh) * 2012-12-14 2015-06-10 清华大学 一种控制曲率分布的离心叶轮流道设计方法
CN103644141B (zh) * 2013-12-20 2015-09-30 中国农业大学 一种获取双吸离心泵叶片载荷分布曲线的方法
CN103925236B (zh) * 2014-03-24 2016-09-14 江苏大学 一种无堵塞旋流泵多工况水力设计方法
CN103994100B (zh) * 2014-05-07 2016-06-29 江苏大学 一种螺旋形单流道无堵塞离心泵叶轮设计方法
JP6488167B2 (ja) * 2015-03-27 2019-03-20 株式会社荏原製作所 渦巻ポンプ
DE102015213451B4 (de) 2015-07-17 2024-02-29 KSB SE & Co. KGaA Kreiselpumpen-Schaufelprofil
DE102016107656A1 (de) * 2016-04-25 2017-10-26 Ebm-Papst Mulfingen Gmbh & Co. Kg Schaufelkantengeometrie einer Schaufel eines Luftförderrads
JP6758923B2 (ja) * 2016-06-01 2020-09-23 株式会社クボタ 羽根車
AU201614369S (en) * 2016-08-12 2016-10-27 Weir Minerals Australia Ltd Impeller
USD810788S1 (en) * 2016-08-25 2018-02-20 Weir Minerals Australia Ltd. Pump impeller
USD810789S1 (en) * 2016-08-25 2018-02-20 Weir Minerals Australia Ltd. Pump impeller
DE102017213507A1 (de) * 2017-08-03 2019-02-07 KSB SE & Co. KGaA Laufrad für Abwasserpumpe
EP3835591B1 (en) * 2019-12-13 2023-08-02 Dab Pumps S.p.A. Impeller for centrifugal pump, particularly for a recessed-impeller pump, and pump with such an impeller
DE102021118564A1 (de) 2021-07-19 2023-01-19 KSB SE & Co. KGaA Schaufelanordnung mit Mikroschaufeln

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DE2525316A1 (de) * 1974-06-13 1975-12-18 Sundstrand Corp Laufrad-anordnung fuer zentrifugalpumpen
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Also Published As

Publication number Publication date
MX2013010939A (es) 2013-12-06
CN103534489A (zh) 2014-01-22
HUE051436T2 (hu) 2021-03-01
BR112013026753A2 (pt) 2019-09-24
RU2013146836A (ru) 2015-05-27
JP6092186B2 (ja) 2017-03-08
AU2012244804A1 (en) 2013-10-17
RU2580237C2 (ru) 2016-04-10
JP2014511973A (ja) 2014-05-19
US9556739B2 (en) 2017-01-31
KR101868132B1 (ko) 2018-06-18
US20140064970A1 (en) 2014-03-06
AU2012244804B2 (en) 2016-02-18
WO2012143367A2 (de) 2012-10-26
DE102011007907B3 (de) 2012-06-21
CA2833193C (en) 2018-08-14
EP2699803A2 (de) 2014-02-26
DK2699803T3 (da) 2020-07-27
CA2833193A1 (en) 2012-10-26
CN103534489B (zh) 2016-12-21
KR20140027130A (ko) 2014-03-06
WO2012143367A3 (de) 2013-01-10
ZA201307151B (en) 2015-04-29

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