EP2734736B1

EP2734736B1 - Improvements to pumps and components therefor

Info

Publication number: EP2734736B1
Application number: EP12815181.8A
Authority: EP
Inventors: Luis Moscoso Lavagna; Garry Bruce Glaves
Original assignee: Weir Minerals Australia Ltd
Current assignee: Weir Minerals Australia Ltd
Priority date: 2011-07-20
Filing date: 2012-07-20
Publication date: 2016-12-28
Anticipated expiration: 2032-07-20
Also published as: EA201391709A1; CN103703254B; CA2839472A1; CN103703254A; HUE031960T2; ZA201309463B; MX341285B; UA112986C2; PE20141349A1; BR112013032290B1; US20140241888A1; IL229958B; CL2013003561A1; CA2839472C; MX2013015045A; EP2734736A1; AU2012286528A1; EP2734736A4; PT2734736T; EA026576B1

Description

Technical Field

This disclosure relates generally to pumps and more particularly, though not exclusively, to centrifugal slurry pumps which are suitable for pumping slurries.

Background of the Disclosure

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. In this latter arrangement, 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. In one form of impeller, 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). As an example, 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 wear in centrifugal slurry pumps that are used for handling coarse particulate slurries typically is worst at the impeller inlet, because the solids have to turn through a right angle (from axial flow in the inlet pipe to radial flow in the pump impeller) and, in so doing, the particle inertia and size results in more impacts and sliding motion against the impeller walls and the leading edge of the impeller vanes.
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.

Summary of the Disclosure

According to the present invention there is provided, in combination, a slurry pump side part and a slurry pump impeller,

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 an impeller rotation axis , the front shroud outer face including an outer region, an inner region and an intermediate region therebetween, the intermediate region being in a plane generally at right angles to the impeller rotation axis and the inner region being inclined towards the pumping vanes;
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, the rear face including an outer region with an outer edge in a plane which is substantially at right angles to the rotation axis, an inner region with an inner edge and an intermediate region between the outer and inner regions which is inclined from the said plane in a direction towards the inlet section, the inner region extending in a direction away from the intermediate region and in a direction away from the front face of the side wall section and generally following the inner region of the outer face of the impeller front shroud,

In certain embodiments 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.
In certain embodiments the inner region comprises a continuous substantially uninterrupted inclined face.
In certain embodiments the intermediate region comprises a continuous substantial uninterrupted inclined face.
In certain embodiments the inclined face of one or both of the intermediate and inner regions is substantially linear.
In certain embodiments one or both of the intermediate and inner regions is generally frusto conical in shape.
In certain embodiments there is a transition region between the intermediate and inner regions, the transition region being curved. In certain embodiments the transition region is generally frusto conical in shape.
In certain embodiments 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.
In certain embodiments 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.
In certain embodiments 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.
In certain embodiments 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.
In certain embodiments 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.
In certain embodiments 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.
In certain embodiments 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.
In certain embodiments 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.
Also disclosed herein is a pump side part for use with a pump impeller, which is outside the scope of the present invention. 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.
In certain examples related to this pump side part not part of the invention 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.
In certain examples related to this pump side part not part of the invention the lateral displacement is inclined inwardly from the said plane in a direction towards the inlet section.
In certain examples related to this pump side part not part of the invention the intermediate region extends from the outer region towards and terminating at the inner region.
In certain examples related to this pump side part not part of the invention the intermediate portion comprises a continuous inclined face. In certain embodiments the inclined face is substantially linear.
In certain examples related to this pump side part not part of the invention the intermediate region is generally frusto conical in shape.
In certain examples related to this pump side part not part of the invention the inner region extends from the intermediate region in a direction away from said front face of said side wall section.
In certain examples related to this pump side part not part of the invention the pump side part further includes a transition region between the intermediate and inner region, the transition region being curved.
In certain examples related to this pump side part not part of the invention the inner region is generally frusto conical in shape.
Also disclosed herein is a pump impeller for use with a pump side part, which is outside the scope of the invention. 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.
In certain examples related to this pump impeller not part of the invention 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.
In certain examples related to this pump impeller not part of the invention the lateral displacement is inclined inwardly from the said plane in a direction towards the pumping vanes.
In certain examples related to this pump impeller not part of the invention the intermediate region extends from the outer edge portion towards and terminating at the inner region.
In certain examples related to this pump impeller not part of the invention the intermediate region comprises a continuous inclined face. In certain embodiments the inclined face is substantially linear.
In certain examples related to this pump impeller not part of the invention the intermediate region is generally frusto conical in shape.
In certain examples related to this pump impeller not part of the invention the pump impeller further includes a plurality of pump-out (or expeller) vanes on the outer face of the front shroud.
Also disclosed herein is a pump impeller in combination with a pump side part, which is outside the scope of the invention. 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.
In certain examples related to this combination not part of the invention the gap is a lateral recess located at a rear face of the side wall section of the pump side part.
In certain embodiments of the combination, the pump side part is as described in the third and fourth aspects.
In certain examples related to this combination not part of the invention 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).
In certain examples related to this combination not part of the invention 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. These various parameters are shown in Figures 8 and 9.
In certain examples related to this combination not part of the invention 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.
In certain examples related to this combination not part of the invention 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.
In certain examples related to this combination not part of the invention 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.
Also disclosed herein is another pump impeller in combination with a pump side part, which is outside the scope of the invention. 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.
Other aspects, features, and advantages will become apparent from the following detailed description when taken in conjunction with the accompanying drawings, which are a part of this disclosure and which illustrate, by way of example, principles of inventions disclosed.

Description of the Figures

The accompanying drawings facilitate an understanding of the various embodiments.

Figure 1 illustrates an exemplary, schematic, partial cross-sectional elevation of a pump incorporating an impeller and an impeller and liner combination, in accordance with one embodiment;
Figure 2 illustrates an exemplary, schematic, partial cross-sectional view of an impeller and pump side part according to another embodiment;
Figures 3 to 7 illustrate various exemplary, schematic, partial cross-sectional views of an impeller and pump side part which are outside the scope of the invention;
Figures 8 and 9 are cross-sectional views of an impeller and pump side part illustration various parameters of the components according to certain embodiments; and
Figures 10 and 11 are exemplary, schematic, partial cross-sectional views of an impeller and pump side part according to a further embodiment, Figure 11 being a more detailed view of that shown in Figure 10.

Detailed Description

Referring to Figure 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.
As best illustrated in Figure 2 and also in the similar embodiment shown in Figures 10 and 11, 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. It is to be understood that 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.
In each embodiment 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. As is the case for the pump side part 30, 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.
In an assembled or operative position 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.
In the embodiment of Figure 2, 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. In this particular embodiment, 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.
In the arrangement of Figure 3, which is outside the scope of the invention, the various regions of the impeller front shroud 50 and the side wall section 15 of the pump side part 30 are generally the same as shown in Figure 2 except in this arrangement the intermediate region of the impeller front shroud 50 is inclined, and the intermediate region of the side wall section 15 is in a plane at right angles to the axis X-X. In this particular arrangement it can be seen that the expeller vanes 56 are also tapered.
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.
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.
In the arrangement of Figure 6, 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.
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.
In the embodiment of Figures 10 and 11, 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.
Various parameters of the pump impeller and side part are illustrated in Figures 8 and 9. These parameters are used in determining the optimum gap size in the region of the transition region.
In order to determine the optimum gap size in the transition region when viewed in cross-section a constructed circle C is generated. The intermediate and inner regions are configured so that they terminate at tangential points 81 and 82 on the circumference of the circle C, and the plane of the outer face of the impeller front shroud is tangential to another point 83 on the circumference of the circle C. Figures 8 and 9 identify the following parameters:

D Diameter of the constructed circle C
Z Outer diameter of the front shroud
Y Inner diameter of innermost end of the inlet section of the pump side part; also being the diameter of the inlet section of the front shroud of the impeller
L Radial distance between Z and Y
M Radial distance from the impeller rotation axis X-X and the centre of circle C
T The depth of the auxiliary or expeller or pump-out vanes 56

The optimum gap size may be determined as follows:

D = 0.02 L to 0.10 L, more preferably 0.04 L to 0.05 L

The optimum position of circle C is as follows:

M = 1.0Y to 1.8Y, or preferably 1.2Y to 1.8Y, or preferably 1.2Y to 1.5Y

In further certain embodiments

D = 0.5 T to 1.5 T, more preferably 0.5 T to 1.0 T

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. In use, 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. Furthermore, in particular with reference to the embodiment shown in Figures 10 and 11, 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.
In the foregoing description of preferred embodiments, specific terminology has been resorted to for the sake of clarity. However, the invention is not intended to be limited to the specific terms so selected, and it is to be understood that each specific term includes all technical equivalents which operate in a similar manner to accomplish a similar technical purpose. Terms such as "front" and "rear", "inner" and "outer", "above", "below", "upper" and "lower" and the like are used as words of convenience to provide reference points and are not to be construed as limiting terms.
The reference in this specification to any prior publication (or information derived from it), or to any matter which is known, is not, and should not be taken as, an acknowledgement or admission or any form of suggestion that prior publication (or information derived from it) or known matter forms part of the common general knowledge in the field of endeavour to which this specification relates.
In this specification, the word "comprising" is to be understood in its "open" sense, that is, in the sense of "including", and thus not limited to its "closed" sense, that is the sense of "consisting only of'. A corresponding meaning is to be attributed to the corresponding words "comprise", "comprised" and "comprises" where they appear.

Claims

In combination, a slurry pump side part (30) and a slurry pump impeller (40),
- the impeller (40) comprising a front shroud (500, a back shroud (51) and a plurality of pumping vanes (42) therebetween, the front shroud (50) having an outer face (54) and an impeller inlet (52) extending through the front shroud (50), the impeller inlet (52) being coaxial with an impeller rotation axis (X-X), the front shroud outer face (54) including an outer region (70), an inner region (72) and an intermediate region (74) therebetween, the intermediate region (74) being in a plane generally at right angles to the impeller rotation axis (X-X) and the inner region being inclined towards the pumping vanes (42);

- the pump side part (30) comprising a side wall section (15) having a front face (36) and a rear face (37), the pump side part (30) further comprising an inlet section (32) extending from the front face (36) and arranged when in use to be coaxial with the impeller rotation axis (X-X), the rear face (37) including an outer region (60) with an outer edge (61) in a plane which is substantially at right angles to the rotation axis (X-X), an inner region (62) with an inner edge (63) and an intermediate region (64) between the outer and inner regions (60, 62) which is inclined from the said plane in a direction towards the inlet section (32), the inner region (62) extending in a direction away from the intermediate region (64) and in a direction away from the front face (36) of the side wall section (15) and generally following the inner region (72) of the outer face (54) of the impeller front shroud (50),
wherein the outer face (54) of the impeller front shroud (500 and the rear face (37) of the pump side part (30) are arranged in use to be facing one another with a gap (80) therebetween the gap having an outer opening (82) and an inner opening (83), the rear face (37) of the side wall section being configured so that the cross-sectional dimension of the gap (80) increases in a direction toward the impeller rotation axis (X-X) in the intermediate region, and the inner region terminating at the inner opening (83).
The combination according to claim 1, wherein the dimension of the gap (80) between the inner region of the outer face (54) of the impeller front shroud (50) and the inner region (62) of the rear face (37) of the pump side part (30) decreases in the direction from the intermediate region (64) towards the inner edge (63).
The combination according to claim 2, wherein the said inner region (62) comprises a continuous substantially uninterrupted inclined face.
The combination according to any one of claims 2 or claim 3, wherein said intermediate region (64) comprises a continuous substantially uninterrupted inclined face.
The combination according to claim 4, wherein the inclined face of one or both of the intermediate (64) and inner regions (62) is substantially linear.
The combination according to claim 4 or 5, wherein one or both of the intermediate and inner regions (64, 62) is generally frusto conical in shape.
The combination according to any one of the preceding claims, further including a transition region (86) between the intermediate and inner regions (64, 62), the transition region (86) being curved.
The combination according to claim 7, wherein said transition region (86) is generally frusto conical in shape.
The combination according to any preceding claim, wherein the rear face (37) has a profile viewed in cross-section in which the profile of the outer region (60), inner region (62) and intermediate region (64) 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 combination according to any preceding claim when appended to claim 7, wherein 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) if an innermost end of the inlet section of the pump side part.
The combination according to claim 10, the diameter (D) of the circle (C) being 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 combination according to claim 10 or claim 11, wherein 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 combination according to claim 10 or claim 11, wherein 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 combination according to claim 10 or 11, wherein 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 combination according to any one of claims 10 to 14, wherein the impeller comprises a plurality of auxiliary vanes (56) 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 combination according to any one of claims 10 to 14, wherein the impeller comprises a plurality of auxiliary vanes (56) on the outer face of the front shroud, the auxiliary vanes being a depth (T), the diameter (D) of the circle (C) being in the range from 0.5 to 1.0 if the depth of the auxiliary vanes.