EP2734736B1 - Verbesserungen an pumpen und bauteile dafür - Google Patents

Verbesserungen an pumpen und bauteile dafür Download PDF

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Publication number
EP2734736B1
EP2734736B1 EP12815181.8A EP12815181A EP2734736B1 EP 2734736 B1 EP2734736 B1 EP 2734736B1 EP 12815181 A EP12815181 A EP 12815181A EP 2734736 B1 EP2734736 B1 EP 2734736B1
Authority
EP
European Patent Office
Prior art keywords
region
impeller
face
side part
front shroud
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
EP12815181.8A
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English (en)
French (fr)
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EP2734736A4 (de
EP2734736A1 (de
Inventor
Luis Moscoso Lavagna
Garry Bruce Glaves
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
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Weir Minerals Australia Ltd
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Priority claimed from AU2011902894A external-priority patent/AU2011902894A0/en
Application filed by Weir Minerals Australia Ltd filed Critical Weir Minerals Australia Ltd
Priority to PL12815181T priority Critical patent/PL2734736T3/pl
Publication of EP2734736A1 publication Critical patent/EP2734736A1/de
Publication of EP2734736A4 publication Critical patent/EP2734736A4/de
Application granted granted Critical
Publication of EP2734736B1 publication Critical patent/EP2734736B1/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
    • 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
    • F04D29/02—Selection of particular materials
    • F04D29/026—Selection of particular materials especially 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
    • F04D29/00—Details, component parts, or accessories
    • F04D29/08—Sealings
    • F04D29/16—Sealings between pressure and suction sides
    • F04D29/165—Sealings between pressure and suction sides especially adapted for liquid pumps
    • F04D29/167—Sealings between pressure and suction sides especially adapted for liquid pumps of a centrifugal flow wheel
    • 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
    • F04D29/2266—Rotors specially for centrifugal pumps with special measures for sealing or thrust balance
    • 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
    • F04D29/2288—Rotors specially for centrifugal pumps with special measures for comminuting, mixing or separating
    • 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
    • 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
    • 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
    • F04D7/045—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 with means for comminuting, mixing stirring or otherwise treating
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2230/00—Manufacture
    • F05D2230/60—Assembly methods

Definitions

  • This disclosure relates generally to pumps and more particularly, though not exclusively, to centrifugal slurry pumps which are suitable for pumping slurries.
  • Centrifugal slurry pumps generally include a pump casing comprising a main casing part and one or more side parts.
  • One of the side parts forms a pump intake which is often referred to as a front liner, suction plate or throatbush.
  • the pump may also comprise an outer housing which encases the pump casing.
  • the pump casing is configured as a pump liner which is typically formed from hard metals or elastomers.
  • An impeller is mounted for rotation within the casing about a rotation axis.
  • the main casing part has an outer peripheral wall section with an internal surface which may be of volute form, a discharge outlet and an inlet which is at one side of the casing and coaxial with the impeller rotation axis.
  • the impeller typically includes a hub to which a 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.
  • two shrouds are provided with pumping vanes being disposed therebetween.
  • the pumping vanes include opposed main side faces one of which is a pumping or pressure side face.
  • the pumping vanes further include a leading edge portion in the region of the inlet and a trailing edge portion in the region of the outer peripheral edge of the or each shroud. The leading edge portion is inclined with respect to the inlet at a vane inlet angle.
  • Centrifugal slurry pumps which may typically comprise hard metal or elastomer liners and/or casing that resist wear, are widely used in the mining industry. Normally, the higher the slurry density, or the larger or harder the slurry particles, will result in higher wear rates and reduced pump life.
  • Centrifugal slurry pumps are widely used in minerals processing plants from the start of the process where the slurry is very coarse with associated high wear rates (for example, during milling), to the end of the process where the slurry is very much finer and the wear rates greatly reduce (for example, when flotation tailings are produced).
  • slurry pumps dealing with a coarser particulate feed duty may only have a life of wear parts measured in weeks or months, compared to pumps at the end of the process which have wear parts which can last from one to two years in operation.
  • the impeller wear occurs mainly on the vanes and the front and rear shrouds at the impeller inlet. High wear in these regions can also influence the wear on the front liner of the pump.
  • the small gap that exists between the rotating impeller and the stationary front liner will also have an effect on the life and performance of the pump wear parts. This gap is normally quite small, but typically increases due to wear on the impeller front, impeller shroud or due to wear on both the impeller and the front liner.
  • One way to reduce the flow that escapes from the high pressure casing region of the pump (through the gap between the front of the impeller and the front liner into the pump inlet) is by incorporating a raised and angled lip on the stationary front liner at the impeller inlet.
  • the impeller has a profile to match this lip.
  • the flow through the gap can also be reduced by the use of expelling vanes on the front of the impeller.
  • the various aspects disclosed herein may be applicable to all centrifugal slurry pumps and particularly to those that experience high wear rates at the impeller inlet or to those that are used in applications with high slurry temperatures.
  • the dimension of the gap between the outer face of the impeller front shroud and the inner region of the rear face of the pump side part decreases in the direction from the intermediate region towards the inner edge.
  • the inner region comprises a continuous substantially uninterrupted inclined face.
  • the intermediate region comprises a continuous substantial uninterrupted inclined face.
  • the inclined face of one or both of the intermediate and inner regions is substantially linear.
  • one or both of the intermediate and inner regions is generally frusto conical in shape.
  • transition region there is a transition region between the intermediate and inner regions, the transition region being curved.
  • the transition region is generally frusto conical in shape.
  • the rear face has a profile viewed in cross-section in which the profile of the outer region, inner region and intermediate region are substantially linear, the outer region profile being substantially at right angles to the central axis, the intermediate region profile being inclined from the outer region profile outwardly with respect to the plane and the inner region profile being inclined inwardly from the intermediate profile with respect to the plane.
  • the gap size in the transition region is determined by a constructed circle C generated in the transition region where the intermediate region and the inner region terminates at respective tangential points on the circumference of the circle, and the plane of the outer face of the impeller front shroud is tangential to another point on the circumference of the circle C, the diameter D of the circle C being in the range from 0.02 to 0.10 of the radial distance L between the outer diameter Z of the front shroud and an inner diameter Y of an innermost end of the inlet section of the pump side part.
  • the diameter D of the circle C is in the range from 0.04 to 0.05 of the radial distance L between the outer diameter Z of the front shroud and an inner diameter Y of an innermost end of the inlet section of the pump side part.
  • the distance M from the centre of the circle C to the rotation axis X-X is from 1.0 to 1.8 of the diameter Y of the innermost end of the inlet section of the pump side part.
  • the distance M from the centre of the circle C to the rotation axis X-X is from 1.2 to 1.8 of the diameter Y of the innermost end of the inlet section of the pump side part.
  • the distance M from the centre of the circle C to the rotation axis X-X is from 1.2 to 1.5 of the diameter Y of the innermost end of the inlet section of the pump side part.
  • the impeller comprises a plurality of auxiliary vanes on the outer face of the front shroud, the auxiliary vanes being of a depth T, the diameter D of the circle C being in the range from 0.5 to 1.5 of the depth of the auxiliary vanes.
  • the impeller comprises a plurality of auxiliary vanes on the outer face of the front shroud, the auxiliary vanes being of a depth T, the diameter D of the circle C being in the range from 0.5 to 1.0 of the depth of the auxiliary vanes.
  • the impeller comprises a front shroud, a back shroud and a plurality of pumping vanes therebetween, the front shroud having an outer face and an impeller inlet extending through the front shroud, the impeller inlet being coaxial with an impeller rotation axis;
  • the pump side part comprising a side wall section, having a front face and a rear face, the pump side part further comprising an inlet section extending from the front face and arranged when in use to be coaxial with the impeller rotation axis, wherein the outer face of the impeller front shroud and the rear face of the pump side part are arranged in use to be facing one another with a gap therebetween, the rear face of the side wall section being configured so that the cross-sectional dimension of the gap increases in a direction toward the impeller rotation axis.
  • the rear face has an outer region with an outer edge in a plane which is substantially at right angles to the central axis and an inner region with an inner edge and the rear face further having an intermediate region between the outer and inner regions which is laterally displaced or recessed from the plane.
  • the lateral displacement is inclined inwardly from the said plane in a direction towards the inlet section.
  • the intermediate region extends from the outer region towards and terminating at the inner region.
  • the intermediate portion comprises a continuous inclined face.
  • the inclined face is substantially linear.
  • the intermediate region is generally frusto conical in shape.
  • the inner region extends from the intermediate region in a direction away from said front face of said side wall section.
  • the pump side part further includes a transition region between the intermediate and inner region, the transition region being curved.
  • the inner region is generally frusto conical in shape.
  • the pump side part comprises a side wall section, a front face and a rear face, an inlet section extending from the front face and arranged when in use to be coaxial with an impeller rotation axis; the impeller comprising a front shroud, a back shroud and a plurality of pumping vanes therebetween, the front shroud having an outer face and an impeller inlet extending through the front shroud, the impeller inlet being coaxial with the impeller rotation axis; wherein the outer face of the impeller front shroud and the rear face of the pump side part are arranged to be facing one another with a gap therebetween, the outer face of the impeller front shroud being configured so that the cross-sectional dimension of the gap increases in a direction toward the impeller rotation axis.
  • the outer face of the front shroud includes an outer region which has an outer edge in a plane which is substantially at right angles to the impeller rotation axis and an inner region with an inner edge; and the outer face further having an intermediate region between the outer and inner regions which is laterally displaced or recessed from the plane.
  • the lateral displacement is inclined inwardly from the said plane in a direction towards the pumping vanes.
  • the intermediate region extends from the outer edge portion towards and terminating at the inner region.
  • the intermediate region comprises a continuous inclined face.
  • the inclined face is substantially linear.
  • the intermediate region is generally frusto conical in shape.
  • the pump impeller further includes a plurality of pump-out (or expeller) vanes on the outer face of the front shroud.
  • the impeller comprises a front shroud, a back shroud and a plurality of pumping vanes therebetween, the front shroud having an outer face and an impeller inlet extending through the front shroud, the impeller inlet being coaxial with an impeller rotation axis; a pump side part comprising a side wall section, a front face and a rear face, an inlet section extending from the front face and arranged when in use to be coaxial with the impeller rotation axis, wherein the outer face of the impeller front shroud and the rear face of the pump side part are arranged to be facing one another with a gap therebetween, one or both of the outer faces of the impeller front shroud and the rear face of the side wall section being configured so that the cross-sectional dimension of the gap is increased when moving in a direction toward the impeller rotation axis.
  • the gap is a lateral recess located at a rear face of the side wall section of the pump side part.
  • the pump side part is as described in the third and fourth aspects.
  • the gap size in the transition region when viewed in cross-section is determined by a constructed circle C generated in the transition region where the intermediate region and the inner region terminates at respective tangential points on the circumference of the circle C, and the plane of the outer face of the impeller front shroud is tangential to another point on the circumference of the circle C, the diameter D of the circle C being in the range from 0.02 to 0.10 of the radial distance L between the outer diameter Z of the front shroud and an inner diameter Y of an innermost end of the inlet section of the pump side part (or the inner diameter of the inlet section of the impeller).
  • the distance M from the centre of the circle C to the rotation axis X-X is from 1.2 to 1.8 of the diameter Y of the innermost end of the inlet section of the pump side part.
  • the impeller comprises a plurality of auxiliary vanes on the outer face of the front shroud, the auxiliary vanes being of a depth T, the diameter of the circle C being in the range from 0.5 to 1.0 of the depth of the auxiliary vanes.
  • the gap size in the transition region when viewed in cross-section is determined by a constructed circle C generated in the transition region where the intermediate region and the inner region terminates at respective tangential points on the circumference of the circle C, and the plane of the outer face of the impeller front shroud is tangential to another point on the circumference of the circle C, the diameter D of the circle C being in the range from 0.02 to 0.10 of the radial distance L between the outer diameter Z of the front shroud and an inner diameter Y of the inlet section of the impeller at the front shroud.
  • the distance M from the centre of the circle C to the rotation axis X-X is from 1.2 to 1.8 of the diameter Y of the inlet section of the impeller at the front shroud.
  • the impeller comprises a front shroud, a back shroud and a plurality of pumping vanes therebetween, the front shroud having an outer face and in impeller inlet extending through the front shroud, the impeller inlet being coaxial with an impeller rotation axis; a pump side part comprising a side wall section, a front face and a rear face, an inlet section extending from the front face and arranged when in use to be coaxial with the impeller rotation axis, wherein the outer face of the impeller front shroud and the rear face of the pump side part are arranged to be facing one another with a gap therebetween, and wherein the gap is configured so that in use material entering thereinto in a direction toward the impeller rotational axis is caused to decelerate as it passes along the gap, thereby reducing erosive wear of the side wall rear face and of the impeller front face.
  • FIG. 1 there is illustrated an exemplary pump 10 in accordance with certain embodiments including a pump casing 12, a back liner or side part 14, a front liner or side part 30 and a pump outlet 18.
  • An internal chamber 20 is adapted to receive an impeller 40 for rotation about a rotational axis X-X.
  • the front liner or side part 30 includes a cylindrically-shaped delivery or inlet section 32 through which slurry enters the pump chamber 20.
  • the inlet or 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 or side part 30 further includes a side wall section 15 which mates with the pump casing 12 to form and enclose the chamber 20, the side wall section 15 having a front face 36 and a rear face 37.
  • the second end 35 of the front liner or side part 30 has a raised lip 38 thereat, with a curvature which is arranged to mate with the impeller 40 at an impeller inlet 52.
  • 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 pumping vanes 42 include a leading edge 43 located at the region of the impeller inlet 48, and a trailing edge 44 located at the region of the impeller outlet 49.
  • the impeller further includes a front shroud 50 with the impeller inlet 52 in the front shroud and a back shroud 51, the vanes 42 being disposed therebetween.
  • the rear face 37 of the side wall section 15 of the pump side part 30 comprises an outer region 60 with an outer edge 61, an inner region 62 with an inner edge 63 and an intermediate region 64 between the inner and outer regions 62 and 60.
  • the outer region 60 may comprise only by the outer edge 61 or it may extend inwardly from the outer edge 61 some distance along the face 37.
  • the side wall section 15 includes an outer face 36 with a rim 69 extending between the inner and outer faces.
  • the outer face may comprise an outer edge 65 of greater diameter than the outer edge 61 of the inner face 37 so that the rim 69 is inclined.
  • the pump side part 30 is arranged to cooperate with an impeller 40 having a front shroud 50 having an inner face 55 and an outer face 54.
  • the outer face 54 comprises an outer region 70, an inner region 72 with an intermediate region 74 therebetween.
  • the outer region 70 has an outer edge 71 and the inner region has an inner edge 73.
  • the outer and inner regions of the impeller front shroud 50 may be comprised by only the outer and inner edges.
  • the impeller may further include auxiliary vanes or expeller vanes or pump-out vanes 56 which extend from the outer edge along the outer face terminating in the intermediate region.
  • the expeller vanes 56 may be of any suitable shape and configuration.
  • the impeller 40 and side part 30 are disposed side by side with the outer face 54 of the impeller 40 facing the rear face 37 of the side part 30 with a gap or space 80 therebetween.
  • the rotation axis of the impeller 40 and the central axis of the pump side part 30 are coaxial.
  • the gap or space 80 provides for an outer opening 82 and an inner opening 83.
  • the outer region 70 of the outer face 54 of the impeller front shroud 50 is comprised by outer edge 71, the intermediate region 74 extends from the outer region 70 or outer edge 71, to the inner region 72.
  • the outer face 64 of the intermediate region 74 is in a plane which is generally at right angles to the impeller rotation axis X-X and the central axis of the side part.
  • the inner region 72 is inclined in a direction away from the front face 36 of the side part 30 and towards the pumping vanes 42.
  • the outer region 60 of the inner face of the side part extends from outer edge 61 to the outer edge 71 of the impeller front shroud 50.
  • the outer region 60 is in a plane at right angles to the axis X-X.
  • the intermediate region 64 extends at an inclined angle from the outer region 60 towards the inner region 62 so that the gap 80 in this region gradually increases in its cross-sectional dimension.
  • the inner region 62 follows generally the inner region of the impeller front shroud 50, there being a transition region 86 between the intermediate 64 and inner 62 regions.
  • Figure 4 The arrangement of Figure 4 is similar to that the embodiment of Figure 2 except that the inner region of the impeller front shroud is in the same plane as the intermediate region; that is, the intermediate region, in effect, continues through to the inner edge 71.
  • Figure 5 The arrangement of Figure 5 is similar to that of Figure 3 except that the inner region of the impeller front shroud is in the same plane as the intermediate region; that is the intermediate region continues through to the inner edge 63.
  • both the intermediate and inner regions of the front shroud and the side wall section are in the same plane, the impeller being in a plane at right angles to the axis X-X and the opposing face of the side wall section being inclined with respect to the shroud.
  • Figure 7 The arrangement of Figure 7 is the same as Figure 6 except that the intermediate and inner regions of the front shroud are inclined and these regions in the pump side part are at right angles to the axis X-X.
  • the part of the gap between the inner (rear) face 37 of the pump side part 30 and the outer face 54 of the impeller 40 is relatively narrow at the outer radius region of the impeller and of the pump side part, and both of the inner face 37 and the outer face 54 are generally at right angles to the impeller rotation axis X-X.
  • This narrow gap region 70 where the faces 37 and 54 are in close alignment extends about one third of the distance between the outer edge 61 and the inner edge 63.
  • the optimum gap size may be determined as follows:
  • the intermediate regions 64 and 74 In the assembled position the intermediate regions 64 and 74 generally face one another with the gap or space therebetween, the gap or space 80 gradually increasing as it extends inwardly.
  • the increase in the dimension of the gap gives a greater cross-sectional area in this region which tends to lower the velocity of fluid including the particles flowing therein, and therefore lowers the abrasive wear on the pump components.
  • the smoothly increasing width configuration of the gap and resultant incremental increase the flow area moving along the intermediate regions yields an optimum reduction in turbulence and abrasive wear of the pump components.
  • the narrow gap portion between the impeller and the outer region of the pump side part improves the sealing performance and wear life of these components.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Claims (16)

  1. Kombination aus einem Dickstoffpumpenseitenteil (30) und einem Dickstoffpumpenlaufrad (40),
    - wobei das Laufrad (40) eine vordere Ummantelung (500), eine hintere Ummantelung (51) und eine Vielzahl von Pumpschaufeln (42) dazwischen umfasst, wobei die vordere Ummantelung (50) eine Außenseite (54) und einen Laufradeinlass (52) aufweist, der sich durch die vordere Ummantelung (50) erstreckt, wobei der Laufradeinlass (52) koaxial mit einer Laufraddrehachse (X-X) ist, wobei die Außenseite (54) der vorderen Ummantelung einen Außenbereich (70), einen Innenbereich (72) und einen Zwischenbereich (74) dazwischen einschließt, wobei der Zwischenbereich (74) auf einer im Allgemeinen zu der Laufraddrehachse (X-X) im rechten Winkel liegenden Ebene liegt und wobei der Innenbereich in Richtung der Pumpschaufeln (42) geneigt ist;
    - der Pumpenseitenteil (30) einen Seitenwandabschnitt (15) umfasst, der eine Vorderseite (36) und eine Rückseite (37) aufweist, wobei das Pumpenseitenteil (30) ferner einen Einlassabschnitt (32) umfasst, der sich von der Vorderseite (36) erstreckt und im Gebrauch angeordnet ist, um mit der Laufraddrehachse (X-X) koaxial zu sein, wobei die Rückseite (37) einen Außenbereich (60) mit einer Außenkante (61) auf einer Ebene, die im Wesentlichen im rechten Winkel zu der Laufraddrehachse (X-X) liegt, einen Innenbereich (62) mit einer Innenkante (63) und einen Zwischenbereich (64) zwischen den Außen- und Innenbereichen (60, 62) einschließt, der von der Ebene in einer Richtung in Richtung des Einlassabschnitts (32) geneigt ist, wobei sich der Innenbereich (62) in eine Richtung weg von dem Zwischenbereich (64) und in einer Richtung weg von der Vorderseite (36) des Seitenwandabschnitts (15) erstreckt und im Allgemeinen dem Innenbereich (72) der Außenseite (54) der vorderen Ummantelung des Laufrads (50) folgt,
    wobei die Außenseite (54) der vorderen Ummantelung des Laufrads (500) und die Rückseite (37) des Pumpenseitenteils (30) im Gebrauch angeordnet sind, um einander mit einem Spalt (80) dazwischen zugewandt zu sein, wobei der Spalt eine äußere Öffnung (82) und eine innere Öffnung (83) aufweist, wobei die Rückseite (37) des Seitenwandabschnitts derart konfiguriert ist, dass sich die Querschnittsabmessung des Spalts (80) in einer Richtung in Richtung der Laufraddrehachse (X-X) in dem Zwischenbereich erhöht und wobei der Innenbereich an der inneren Öffnung (83) endet.
  2. Kombination nach Anspruch 1, wobei die Abmessung des Spalts (80) zwischen dem Innenbereich der Außenseite (54) der vorderen Ummantelung des Laufrads (50) und dem Innenbereich (62) der Rückseite (37) des Pumpenseitenteils (30) in der Richtung von dem Zwischenbereich (64) in Richtung der Innenkante (63) abnimmt.
  3. Kombination nach Anspruch 2, wobei der Innenbereich (62) eine durchgehende, im Wesentlichen ununterbrochene Schrägfläche umfasst.
  4. Kombination nach einem der Ansprüche 2 oder 3, wobei der Zwischenbereich (64) eine durchgehende, im Wesentlichen ununterbrochene Schrägfläche umfasst.
  5. Kombination nach Anspruch 4, wobei die Schrägfläche einer oder beider der Zwischen- (64) und Innenbereiche (62) im Wesentlichen linear ist.
  6. Kombination nach einem der Ansprüche 4 oder 5, wobei eine oder beide der Zwischen- und Innenbereiche (64, 62) im Allgemeinen kugelstumpfförmig ist bzw. sind.
  7. Kombination nach einem der vorhergehenden Ansprüche, die ferner einen Übergangsbereich (86) zwischen den Zwischen- und Innenbereichen (64, 62) einschließt, wobei der Übergangsbereich (86) gekrümmt ist.
  8. Kombination nach Ansprüche 7, wobei der Übergangsbereich (86) im Allgemeinen kugelstumpfförmig ist.
  9. Kombination nach einem der vorhergehenden Ansprüche, wobei die Rückseite (37) ein im Querschnitt gesehenes Profil aufweist, in dem die Profile des Außenbereichs (60), des Innenbereichs (62) und des Zwischenbereichs (64) im Wesentlichen linear sind, wobei das Profil des Außenbereichs im Wesentlichen im rechten Winkel zu der Mittelachse liegt, wobei das Profil des Zwischenbereiches bezogen auf die Ebene von dem Profil des Außenbereichs nach außen geneigt ist und wobei das Profil des Innenbereichs bezogen auf die Ebene von dem Profil des Zwischenbereichs nach innen geneigt ist.
  10. Kombination nach einem der vorhergehenden Ansprüche, bei Abhängigkeit von Anspruch 7, wobei die Spaltgröße in dem Übergangsbereich durch einen konstruierten Kreis (C) festgelegt ist, der in dem Übergangsbereich erzeugt ist, wo der Zwischenbereich und der Innenbereich an entsprechenden Tangentialpunkten auf dem Umfang des Kreises enden, und die Ebene der Außenseite der vorderen Ummantelung des Laufrads zu einem anderen Punkt auf dem Umfang des Kreises (C) tangential ist, wobei der Durchmesser (D) des Kreises (C) in dem Bereich zwischen 0,02 und 0,10 des radialen Abstands (L) zwischen dem Außendurchmesser (Z) der vorderen Ummantelung und einem Innendurchmesser (Y) eines innersten Endes des Einlassabschnitts des Pumpenseitenteils liegt.
  11. Kombination nach Anspruch 10, wobei der Durchmesser (D) des Kreises (C) in dem Bereich zwischen 0,04 und 0,05 des radialen Abstands (L) zwischen dem Außendurchmesser (Z) der vorderen Ummantelung und einem Innendurchmesser (Y) eines innersten Endes des Einlassabschnitts des Pumpenseitenteils liegt.
  12. Kombination nach Anspruch 10 oder Anspruch 11, wobei der Abstand (M) von dem Mittelpunkt des Kreises (C) zu der Drehachse (X-X) zwischen 1,0 und 1,8 des Durchmessers (Y) des innersten Endes des Einlassabschnitts des Pumpenseitenteils liegt.
  13. Kombination nach Anspruch 10 oder Anspruch 11, wobei der Abstand (M) von dem Mittelpunkt des Kreises (C) zu der Drehachse (X-X) zwischen 1,2 und 1,8 des Durchmessers (Y) des innersten Endes des Einlassabschnitts des Pumpenseitenteils liegt.
  14. Kombination nach Anspruch 10 oder 11, wobei der Abstand (M) von dem Mittelpunkt des Kreises (C) zu der Drehachse (X-X) zwischen 1,2 und 1,5 des Durchmessers (Y) des innersten Endes des Einlassabschnitts des Pumpenseitenteils liegt.
  15. Kombination nach einem der Ansprüche 10 bis 14, wobei das Laufrad eine Vielzahl von Hilfsschaufeln (56) an der Außenseite der vorderen Ummantelung aufweist, wobei die Hilfsschaufeln von einer Tiefe (T) sind, wobei der Durchmesser (D) des Kreises (C) in dem Bereich zwischen 0,5 und 1,5 der Tiefe der Hilfsschaufeln liegt.
  16. Kombination nach einem der Ansprüche 10 bis 14, wobei das Laufrad eine Vielzahl von Hilfsschaufeln (56) an der Außenseite der vorderen Ummantelung aufweist, wobei die Hilfsschaufeln von einer Tiefe (T) sind, wobei der Durchmesser (D) des Kreises (C) in dem Bereich zwischen 0,5 und 1,0 der Tiefe der Hilfsschaufeln liegt.
EP12815181.8A 2011-07-20 2012-07-20 Verbesserungen an pumpen und bauteile dafür Active EP2734736B1 (de)

Priority Applications (1)

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PL12815181T PL2734736T3 (pl) 2011-07-20 2012-07-20 Usprawnienia pompy i jej podzespołów

Applications Claiming Priority (2)

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AU2011902894A AU2011902894A0 (en) 2011-07-20 Improvements to pumps and components therefore
PCT/AU2012/000868 WO2013010224A1 (en) 2011-07-20 2012-07-20 Improvements to pumps and components therefor

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EP2734736A1 EP2734736A1 (de) 2014-05-28
EP2734736A4 EP2734736A4 (de) 2015-01-14
EP2734736B1 true EP2734736B1 (de) 2016-12-28

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EP (1) EP2734736B1 (de)
CN (1) CN103703254B (de)
AP (1) AP2013007329A0 (de)
AU (1) AU2012286528B2 (de)
BR (1) BR112013032290B1 (de)
CA (1) CA2839472C (de)
CL (1) CL2013003561A1 (de)
EA (1) EA026576B1 (de)
ES (1) ES2620760T3 (de)
HU (1) HUE031960T2 (de)
IL (1) IL229958B (de)
MX (1) MX341285B (de)
PE (1) PE20141349A1 (de)
PL (1) PL2734736T3 (de)
PT (1) PT2734736T (de)
UA (1) UA112986C2 (de)
WO (1) WO2013010224A1 (de)
ZA (1) ZA201309463B (de)

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GB2542233B (en) * 2015-08-26 2018-02-07 Weir Minerals Europe Ltd Rotary parts for a slurry pump
JP7275259B2 (ja) * 2017-10-12 2023-05-17 ウィアー・ミネラルズ・オーストラリア・リミテッド スラリーポンプ用の入口構成要素
US11236763B2 (en) * 2018-08-01 2022-02-01 Weir Slurry Group, Inc. Inverted annular side gap arrangement for a centrifugal pump

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US4613281A (en) * 1984-03-08 1986-09-23 Goulds Pumps, Incorporated Hydrodynamic seal
US4913619A (en) * 1988-08-08 1990-04-03 Barrett Haentjens & Co. Centrifugal pump having resistant components
FR2698666B1 (fr) * 1992-11-30 1995-02-17 Europ Propulsion Pompe centrifuge hautement performante à rouet ouvert.
AUPN715595A0 (en) * 1995-12-14 1996-01-18 Warman International Limited Improved centrifugal pump
JP3179716B2 (ja) * 1996-10-29 2001-06-25 株式会社荏原製作所 キャンドモータポンプ
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BR112013032290A2 (pt) 2016-12-20
EP2734736A4 (de) 2015-01-14
HUE031960T2 (en) 2017-09-28
PE20141349A1 (es) 2014-10-13
CL2013003561A1 (es) 2014-11-14
AP2013007329A0 (en) 2013-12-31
MX341285B (es) 2016-08-12
MX2013015045A (es) 2014-02-17
CN103703254B (zh) 2016-12-28
US20140241888A1 (en) 2014-08-28
EA026576B1 (ru) 2017-04-28
ZA201309463B (en) 2021-08-25
CA2839472C (en) 2019-10-01
ES2620760T3 (es) 2017-06-29
PL2734736T3 (pl) 2017-07-31
EA201391709A1 (ru) 2014-04-30
EP2734736A1 (de) 2014-05-28
WO2013010224A1 (en) 2013-01-24
CN103703254A (zh) 2014-04-02
UA112986C2 (uk) 2016-11-25
AU2012286528B2 (en) 2016-04-21
AU2012286528A1 (en) 2013-05-02
IL229958B (en) 2019-09-26
PT2734736T (pt) 2017-03-30
BR112013032290B1 (pt) 2021-05-18
CA2839472A1 (en) 2013-01-24

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