EP2978975B1 - Slurry pump impeller - Google Patents

Slurry pump impeller Download PDF

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Publication number
EP2978975B1
EP2978975B1 EP14774127.6A EP14774127A EP2978975B1 EP 2978975 B1 EP2978975 B1 EP 2978975B1 EP 14774127 A EP14774127 A EP 14774127A EP 2978975 B1 EP2978975 B1 EP 2978975B1
Authority
EP
European Patent Office
Prior art keywords
face
edge
side face
trailing edge
leading edge
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
EP14774127.6A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP2978975A4 (en
EP2978975A1 (en
Inventor
Craig Ian Walker
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.)
Weir Minerals Australia Ltd
Original Assignee
Weir Minerals Australia Ltd
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
Priority claimed from AU2013901086A external-priority patent/AU2013901086A0/en
Application filed by Weir Minerals Australia Ltd filed Critical Weir Minerals Australia Ltd
Priority to PL14774127T priority Critical patent/PL2978975T3/pl
Publication of EP2978975A1 publication Critical patent/EP2978975A1/en
Publication of EP2978975A4 publication Critical patent/EP2978975A4/en
Application granted granted Critical
Publication of EP2978975B1 publication Critical patent/EP2978975B1/en
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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
    • F04D29/2261—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
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D7/00—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts
    • F04D7/02—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts of centrifugal type
    • F04D7/04—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts of centrifugal type the fluids being viscous or non-homogenous

Definitions

  • This disclosure relates generally to impellers for centrifugal slurry pumps.
  • Slurries are usually a mixture of liquid and particulate solids, and are commonly found in the minerals processing, sand and gravel and/or dredging industry.
  • Centrifugal slurry pumps generally include a pump casing having a pumping chamber therein which may be of a volute configuration with an impeller mounted for rotation within the pumping chamber.
  • a drive shaft is operatively connected to the pump impeller for causing rotation thereof, the drive shaft entering the pump casing from one side.
  • the pump further includes a pump inlet which is typically coaxial with respect to the drive shaft and located on the opposite side of the pump casing to the drive shaft. There is also a discharge outlet typically located at a periphery of the pump casing.
  • the pump casing may be in the form of a liner which is encased within an outer pump housing.
  • the impeller typically includes a hub to which the drive shaft is operatively connected, and at least one shroud. Pumping vanes are provided on one side of the shroud with discharge passageways between adjacent pumping vanes.
  • the impeller may be of the closed type where two shrouds are provided with the pumping vanes being disposed therebetween.
  • the impeller may however be of the "open" face type which comprises one shroud only.
  • US 2010/0284812 discloses a centrifugal water pump having an impeller which has aerofoil shaped vanes with a thick base (portion in contact with back shroud) tapering to a thin tip (portion closest to the fluid inlet). Although the vanes are twisted along their length, they would not be suitable for use in slurry pumps.
  • the vanes of D2 are typical of the mixed flow type, that is the vanes are of a double curvature type.
  • the patent is concerned with a novel method to produce such a vane.
  • EP2570674 describes an erosion restraint impeller vane made of metallic laminate, the vane comprising a first metallic core material and a wear resistant material, the hardness of the wear resistant material being higher than that of the metallic core material.
  • slurry pumps handling heterogeneous slurries (with settling particles of typical size 0.5mm) it is common for there to be solids concentration gradients throughout the flows in the inlet pipe and within the impeller and pump casing.
  • concentration gradients are caused by the various forces acting on the particle including: gravity, fluid drag and centrifugal forces.
  • the slurry particles are at their highest concentration at the root of the vane on the back shroud of the impeller, that is, in the region where a side edge of the vane contacts the shroud.
  • a pump impeller which includes:
  • the configuration of the vane is such that in use the Coriolis force generated by the vane disperses particles across that vane at its trailing edge thereby reducing wear near the region where the vane abuts against the face of the back shroud.
  • the first side face at the trailing edge is in a plane which is at an obtuse angle in a range of greater than about 90° to about 135°. In certain embodiments, the first side face at the leading edge is in a plane which is at an acute angle in a range of about 45° to less than about 90°.
  • the angle of the first side face progressively changing when moving from the leading edge to the trailing edge of the vane may be in a continuous form of curvature when moving from the leading edge to the trailing edge, or in multiple straight sectors at different acute or obtuse angles to form the shape of the pumping vane.
  • the first side face is a leading face with respect to the direction of rotation, so that fluid being pumped is impacted against it.
  • each pumping vane includes a leading edge section terminating at the leading edge the leading edge section tapering inwardly towards the leading edge, and a trailing edge section terminating at the trailing edge the trailing edge section tapering inwardly towards the trailing edge, each pumping vane including a main section between the leading and trailing edge sections which has a width or thickness which is generally constant from one side edge thereof to an opposed side edge and along its length from the leading edge section to the trailing edge section.
  • the first side face is configured such that the surface thereof, at any line between the leading and trailing edges which is at 90° from one side edge to the other, is flat or linear in the direction of that line.
  • the first side face is a face of a rectangular flat strip with the leading edge and trailing edge forming two shorter sides of the rectangular flat strip and side edges forming two longer sides of the rectangular flat strip, said rectangular flat strip being twisted about an axis extending from the leading edge to the trailing edge, said rectangular flat strip also being curved between the leading edge and the trailing edge such that the first side face is backward-curved and the first side face of the rectangular flat strip is linear or flat in the direction of a line which is drawn from one side edge to the other at any point between the leading edge and the trailing edge of the first side face where the line meets each of the side edges at an angle of 90°.
  • the pumping vanes are curved in a lengthwise direction between the leading and trailing edges although in some other embodiments the impeller pumping vanes can be straight along their distal length.
  • the vanes are backwardly curved with respect to the direction of rotation of the impeller, although for some applications the direction of curvature may be forwardly curved with respect to the direction of rotation of the impeller, depending on the nature of fluid.
  • a pump impeller which includes:
  • FIG. 1 there is illustrated a typical example of a pump 10 which includes a pump casing or volute 12, a back liner 14, a front liner 30 and a pump outlet 18.
  • An internal chamber 20 is adapted to receive an impeller 40 for rotation about rotational axis X-X.
  • the front liner 30 includes a cylindrically-shaped delivery section 32 through which slurry enters the pump chamber 20.
  • the delivery section 32 has a passage 33 therein with a first, outermost end 34 operatively connectable to a feed pipe (not shown) and a second, innermost end 35 adjacent the chamber 20.
  • the front liner 30 further includes a side wall section 15 which mates in use with the pump casing 12 to form and enclose the chamber 20, the side wall section 15 having an inner face 37.
  • the second end 35 of the front liner 30 has a raised lip 38 thereat, which is arranged in a close facing relationship with the impeller 40.
  • the impeller 40 includes a hub 41 from which a plurality of circumferentially spaced pumping vanes 42 extend. An eye portion 47 extends forwardly from the hub towards the passage 33 in the front liner.
  • the impeller further includes a front shroud 50 and a back shroud 51, the vanes 42 being disposed therebetween.
  • the pumping vanes include a leading edge section 60 having a leading edge 43 and a trailing edge section 61 having a trailing edge 44.
  • the leading edge section 60 is tapered inwardly towards the leading edge 43 and the trailing edge section 61 is tapered inwardly towards the trailing edge 44.
  • the pumping vanes have a main section 63 between the leading edge section 60 and trailing edge section 61 which at any planar height above the back shroud 51 has a width or thickness 64 which is generally constant from one side edge 56 to the other side edge 57 and along its length from the leading edge section 60 to the trailing edge section 61.
  • the pumping vane 42 is generally arcuate in cross-section and includes an inner leading edge 43 and an outer trailing edge 44, opposed side edges 56, 57 and opposed first and second faces 45, 46 between the side edges 56, 57, the face 45 being a pumping or pressure side face.
  • the vanes of this type are normally referred to as backward-curving vanes when viewed with the direction of rotation.
  • the side edge 56, 57 are disposed against respective inner faces of the shrouds 50, 51.
  • the inner faces 53, 54 are generally at right angles to the central rotation axis X-X.
  • the face 45 which is a pumping or pressure side face of the pumping vane 42 is configured such that the surface thereof at any line between the leading and trailing edges 43, 44 which is at 90° from one side edge 56 to the other 57 is flat or linear in the direction of that line.
  • the face 45 may be likened to a face of a rectangular flat strip with the leading edge 43 and the trailing edge 44 forming the two shorter sides of the rectangular flat strip and the side edges 56, 57 each forming the two respective longer sides of the rectangular flat strip.
  • the rectangular flat strip is twisted about an axis that extends from the leading edge 43 to the trailing edge 44.
  • the rectangular flat strip is also curved between the leading edge 43 and the trailing edge 44 which provides that face 45 is backward-curved.
  • a face (that is face 45) of the rectangular flat strip that is twisted and curved in this way, is linear or flat in the direction of a line which is drawn from one longer side (that is side edge 56) to the other longer side (that is side edge 57) at any point between the two shorter sides (that is the leading edge 43 and the trailing edge 44) of the rectangular flat strip when the line meets each of the longer sides at an angle of 90°.
  • the first face 45 is flat or linear when viewed at any cross-section along its length from the leading edge 43 to the trailing edge 44, each cross-section being taken at rights angles to the side edges 56, 57 of the vane. Examples of such cross-sections are illustrated in Figures 3 to 5 showing cross-sections taken along the lines 1, 2, and 3 in Figure 2 . As is apparent from viewing these Figures, the first face 45 is flat or linear at these cross sections. Described in another way, it means that the first face 45 is not bowed or convex at any of the cross-sectional views in question. In the embodiment described, the second face 46 is also flat or linear when viewed at any cross section.
  • the angle of inclination Y of the side face 45 with respect to the main inner face 53 of the back shroud 51 progressively changes along the length of the vane 42 when moving from its leading edge 43 to its trailing edge 44.
  • This change in angle is clearly shown in Figures 3 to 5 .
  • the angle of inclination Y is also referred to as the leading angle of the vane with respect to the direction of rotation of the impeller in use.
  • the angle of inclination Y is an acute angle at the leading edge 43.
  • the angle is in a range from about 45° to less than 90°, more preferably the angle is in a range from about 70° to about 80°, and more preferably is about 75°.
  • the angle progressively changes and, at the position shown in Figure 4 , it is at right angles (perpendicular).
  • the angle of inclination is obtuse.
  • the angle at the trailing edge is in a range from greater than 90° up to about 135°, more preferably the angle is in a range from about 100° to about 130°, and more preferably is about 110°.
  • the Coriolis force (Arrow B in Figure 2 ), which is generated as a result of the in use rotation of the impeller in the direction of arrow A in Figure 2 , causes the particulates C in a slurry or fluid which is being conveyed by the pump impeller of the present embodiment, to disperse over the face of the vane as the particulates travel along the vane from the leading edge to the trailing edge.
  • the vane shape arrangement can assist to break up solid particle concentration gradients within the impeller where the slurry particles are at their highest concentration at the root of the vane on the back shroud of the impeller, that is, in the region where a side edge of the vane contacts the shroud. This can result in a reduction of the wear due to grooving of the impeller at that point.
  • Figures 6 , 7 , 8 and 9 illustrate an impeller according to one embodiment.
  • the same reference numerals as used to identify parts in Figures 1 , 2 , 3 , 4 and 5 are used to identify similar parts in the embodiment of Figures 6 , 7 , 8 and 9 .
  • Figures 6 and 7 depict portions of an impeller 40 from different sides looking into the discharge passageways between the vanes 42, and Figures 8 and 9 each show an impeller 40 in its entirety.
  • the angle of inclination of the side face 45 with respect to the main inner face 53 of the back shroud 51 progressively changes along the length of the vanes 42 when moving from the leading edge (now shown) to its trailing edge 44.
  • Figure 10 illustrates a modified form of the arrangement shown in Figure 2 .
  • the same reference numerals as used to identify parts in Figure 2 are used to identify similar parts in the modified form of Figure 10 .
  • the change in the angle of inclination Y along the length of the vane 42 as shown in Figure 10 is greater than the change in the angle of inclination Y along the length of the vane 42 as shown in Figure 2 .

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Geometry (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
EP14774127.6A 2013-03-28 2014-03-28 Slurry pump impeller Active EP2978975B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PL14774127T PL2978975T3 (pl) 2013-03-28 2014-03-28 Wirnik napędzany pompy szlamowej

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
AU2013901086A AU2013901086A0 (en) 2013-03-28 Slurry pump impeller
PCT/AU2014/000337 WO2014153616A1 (en) 2013-03-28 2014-03-28 Slurry pump impeller

Publications (3)

Publication Number Publication Date
EP2978975A1 EP2978975A1 (en) 2016-02-03
EP2978975A4 EP2978975A4 (en) 2016-11-09
EP2978975B1 true EP2978975B1 (en) 2019-01-02

Family

ID=51622284

Family Applications (1)

Application Number Title Priority Date Filing Date
EP14774127.6A Active EP2978975B1 (en) 2013-03-28 2014-03-28 Slurry pump impeller

Country Status (17)

Country Link
US (1) US20160040682A1 (zh)
EP (1) EP2978975B1 (zh)
CN (1) CN105074225B (zh)
AP (1) AP2015008763A0 (zh)
AU (1) AU2014245856B2 (zh)
BR (1) BR112015024718A2 (zh)
CA (1) CA2902759A1 (zh)
CL (1) CL2015002887A1 (zh)
EA (1) EA031306B1 (zh)
ES (1) ES2709199T3 (zh)
MX (1) MX365143B (zh)
PE (1) PE20151584A1 (zh)
PH (1) PH12015501912B1 (zh)
PL (1) PL2978975T3 (zh)
PT (1) PT2978975T (zh)
TR (1) TR201901181T4 (zh)
WO (1) WO2014153616A1 (zh)

Families Citing this family (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9599120B2 (en) * 2012-08-24 2017-03-21 Asmo Co., Ltd. Impeller for centrifugal pump and centrifugal pump of vehicle washer device
GB2542233B (en) * 2015-08-26 2018-02-07 Weir Minerals Europe Ltd Rotary parts for a slurry pump
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
AU201614664S (en) 2016-08-25 2016-11-08 Weir Minerals Australia Ltd Pump impeller
CN107299910B (zh) * 2017-07-07 2019-10-18 安徽卧龙泵阀股份有限公司 一种化工离心泵叶轮装置
USD847863S1 (en) * 2017-12-20 2019-05-07 Crane Pumps & Systems, Inc. Slicer blade and striker plate assembly for a centrifugal pump
CN108561330A (zh) * 2018-06-29 2018-09-21 浙江南元泵业有限公司 离心泵叶轮
MA53344A (fr) * 2018-08-01 2021-11-10 Weir Slurry Group Inc Agencement d'espace latéral annulaire inversé pour pompe centrifuge
CN213808111U (zh) * 2020-08-27 2021-07-27 芜湖美的厨卫电器制造有限公司 叶轮、水泵和热水器

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20100284812A1 (en) * 2009-05-08 2010-11-11 Gm Global Technology Operations, Inc. Centrifugal Fluid Pump

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FR2640328B1 (fr) * 1988-12-09 1991-03-15 Schlumberger Cie Dowell Rotor a pales pour pompe du type centrifuge, pompe et melangeur en faisant application
US5730582A (en) * 1997-01-15 1998-03-24 Essex Turbine Ltd. Impeller for radial flow devices
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CN2412114Y (zh) * 1999-03-11 2000-12-27 王庆武 排沙水泵叶轮
ITMI20012414A1 (it) * 2001-11-15 2003-05-15 Nuovo Pignone Spa Pala per girante di compressore centrifugo a medio-alto coefficiente di flusso
US8037713B2 (en) * 2008-02-20 2011-10-18 Trane International, Inc. Centrifugal compressor assembly and method
CN201288694Y (zh) * 2008-10-07 2009-08-12 石家庄工业水泵有限公司 一种高效渣浆泵
CN101368574A (zh) * 2008-10-15 2009-02-18 许洪元 两相流泵叶轮的设计方法
EP2497956A1 (de) * 2011-03-08 2012-09-12 Egger Pumps Technology AG Freistrompumpe
EP2570674A1 (en) * 2011-09-15 2013-03-20 Sandvik Intellectual Property AB Erosion resistant impeller vane made of metallic laminate
JP5879103B2 (ja) * 2011-11-17 2016-03-08 株式会社日立製作所 遠心式流体機械
DE102012209832B3 (de) * 2012-06-12 2013-09-12 E.G.O. Elektro-Gerätebau GmbH Pumpe und Verfahren zum Herstellen eines Impellers für eine Pumpe

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Publication number Priority date Publication date Assignee Title
US20100284812A1 (en) * 2009-05-08 2010-11-11 Gm Global Technology Operations, Inc. Centrifugal Fluid Pump

Also Published As

Publication number Publication date
CA2902759A1 (en) 2014-10-02
PE20151584A1 (es) 2015-11-18
PL2978975T3 (pl) 2019-06-28
PH12015501912A1 (en) 2016-01-11
BR112015024718A2 (pt) 2017-07-18
ES2709199T3 (es) 2019-04-15
EP2978975A4 (en) 2016-11-09
EP2978975A1 (en) 2016-02-03
AU2014245856A1 (en) 2015-09-17
MX365143B (es) 2019-05-24
AP2015008763A0 (en) 2015-09-30
PT2978975T (pt) 2019-02-08
TR201901181T4 (tr) 2019-02-21
EA031306B1 (ru) 2018-12-28
MX2015013549A (es) 2016-04-07
EA201591520A1 (ru) 2016-01-29
PH12015501912B1 (en) 2016-01-11
US20160040682A1 (en) 2016-02-11
WO2014153616A1 (en) 2014-10-02
AU2014245856B2 (en) 2018-02-15
CN105074225B (zh) 2017-02-15
CL2015002887A1 (es) 2016-05-20
CN105074225A (zh) 2015-11-18

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