CA1193485A - High head centrifugal slicing slurry pump - Google Patents

Abstract

Applicant: Vaughan Co., Inc.
Title, High Head Centrifugal Slicing Slurry Pump ABSTRACT
A booster propeller is located at the inlet of a flared funnel leading toward arcuate inlet apertures in an end plate of a centrifugal pump casing. The pump impeller is received in a howl capped by the end plate and has a circular shroud plate perpendicular to the axis with vanes or blades projecting toward the end plate and having cupped leading surfaces forming a sharpened edge. Such blades are swept back in the area of the end plate inlet apertures for effective slicing of chunks or lumps of solid material in the slurry in combination with sharpened leading edges of the inlet apertures.
The pump casing bowl has a circumferential outlet and the end plate is recessed into the open end of the bowl so that the inner face of the end plate is flush with the adjoining face of the outlet for smooth flow of material into the outlet,

Description

This application i5 a division of Canadian application Serial No. 391 r172~ filed November 30~
1981, for High Head Centrifugal Slicing Sll~rry Pump.
The present invention relates to centri~ugal pumps and particularly to centrifugal pumps effective for pumping slurries of liquid9 usually water~ and suspended solids constituting up to about 25 percen~
by weight oE such slurries. Usually, the slurries have chunks or lumps of solid material that could clog or otherwise reduce the efficiency of a centrifugal pump so that such slurry pumps must have mechanism for comminuting th~ lumps or chunks to ensure effective and consistent pumping of the slurry.
The pump of the present invention is of the same general type as the "CentriEugal Chopping Slurry Pump" disclosed in Vaughan U.S~ patent No~ 3r973~866 issued Au~ust 10, 1976, which is stated to be an improvement on the general type of pump disclosed in Vaughan U.S. patent No~ 3,155,046, issued November 3, 1964~ The pumps of both of those patents are designed for pumping slurries containing chunks or lumps of solid material.
In general, each of the prior pumps has an upright drive shaft, the lower end portion of which projects downward into a substantially cylindrical pump casingO The impeller Eixed to the drive shaft within the casing has a radial shroud disc or plate with downward projecting~ gerlerally radially extending blades or ~anes. The bottom of the casing is closed by an end plate having arcuate inlet apertures for J~

intake of slurry in an axial direction. The sharpened lower edges of the impeller blades cooperate with the leading edges of the inlet apertures for chopping chunks or lumps of solid material in the slurry ~eing pumped~ The slurry is accelerated circumferentially and outward to a generally tangential outlet conduit.
The pump disclosed in UOSO patent NoO
3,973,866 also includes a screw propeller cantilevered from the pump drive shaft outside the pump casing and adjacent to the inlet apertures in the end plateO
Such propeller has generally radial blades with somewhat sharpened leading edges for chopping chunks or lumps in the slurry, In addition, the screw propeller is stated to generate a positive current flow of slurry through the end plate inlet aperturesO
Another aspect of the pump of U.S~ patent No. 3,973,866 that is pertinent to the present invention is the use of elongated "slinger" ribs or vanes of small axial height projecting from the side of the impeller shroud plate opposite the lower primary pumping impeller blades. Such upper vanes are in the form of volute ribs for slinging away from the drive shaft bearing structure the solid material component of slurry which may work its way past the edge of the shroud plate so as to reduce wear of such bearing structure. See the paragraph beginning at column 2, line 21.
The prior pumps are of relatively low head and efficiency as compared to the pump of the present invention. In such pumps flow through the end plate inlet apertures into the impeller~receiving pump casing and out of the casing through the pump outlet ~3~

is much more turbulent than in the pump of the present inven t ion O
In accordance with the present invention t improvements made to the pump disclosed in U,S~ patent NoO 3,973,866 include: changing the design of the bottom booster propeller so as to increase the head of the pump without decreasing the chopping effectiveness of such propeller; locating the booster propeller at khe entrance to a downwardly flared funnel -for effecting smooth gradual acceleration of slurry toward the inlet apertures; locating the inlet apertures closer to the axis of rotation of the i.mpeller so as to eliminate ox greatly reduce backflow of high-pressure slurry in the radially outer portion of the pump casing and increase the efectiveness of the impeller vanes to accelerate outward movement of the slurry; rounding the entrances to fair the inlet apertures for smooth flow into the pump casing;
enclosing the impeller in a semicylindrical, semivolute casing~ the volute portion being located immediately rearward of the pump outlet; sweeping back the impeller blades for providing an improved slicing action of th~ sharpened lower edges vf the blades .in cooperation with sharpened forward edges of the inlet apertures; decreasing the thickness of the impeller blades relative to the radial width of the inlet apertures so as not to intexfere wi.th intake of slurry through the inlet apertures; merging the impeller blades inko the shroud plate with fillets for smooth, substantially nonturbulent acceleration of the slurry circumferentially and outward towa.rd the pump ou-tlet J
cupping the leading Eaces of the impeller blades to ~3-~ 3~3~
ensure smooth change of direction of the slurry and effective slicing of chunks or lumps of solid material in the slurry; recessing the apertured ~nd plate into the pump casing to dispose it:s inner surface flush with the adjoining surface of the pump outlet for smoother flow of slurry into the pump outlet; and arranging the upper "slinger" ribs or vanes for producing a slight suction in the area of the drive shaft seal for increasing the lif~ of the seal and to enable quick and accurate detection of seal failure.
The principa.l object of the present invention is to provide an efficient, durable centrifugal pump having a high head characteristic and adapted t~
consistently pump slurry containing solid chunks or lumps.
This object can be accomplished in part by providing in a centrifugal pump, the improvement comprising the combination of a pump casing forming a bowl of generally circular cross section and having a substantially closed end~ an open end and a circumferential outlet, an impeller received in said bowl r rotatable therein and having pumping vanes projecting toward said open end of said casing, drive shaft means extending generally axially through said substantially closed end of said casing and caxrying said impellerr an end plate rec~ssed into and closely fitted .in said open end of said casing so that the inner face of said end plate adjacent to said impeller is flush with the adjacen-t face of said circumferential outlet~ the outer face of said end plate forming an outwardly flared funnel and said end plate having an inlet at the base of said funnel for intake of material into said casing, a booster p:ropeller coaxial with said impeller and located outside said casing 7 and spacer means journaled in said end plate at th~ base of said funnel, interconnecting said impeller and said booster propeller for conjoint rotation and positioning said booster propeller at approximately the entranse of said funnel.
In drawings which illustrate an embodiment of the invention:
Figure 1 is a side elevation of a centrifugal slicing slurry pump in accordance with the present invention with parts broken away and parts shown in section;
Figure 2 is a bottom plan of the pump of Figure 1;
Figure 3 is a somewhat dlagrammaticO
fragmentary, top perspective of a component of the pump of Figure 1, namely, the c~isintegrator or booster propeller, showing its mounting structure in phantom;
Figure 4 is a section taken on line 4--4 of Figure 3 but on a larger scale;
Figure 5 is a section taken on line 5--5 of Figure 1 with parts broken away;
Figure 6 is a fragmentary s~ction taken on line 6--6 of Figure 5; and Figure 7 is a fragmentary~ detail section taken on line 7--7 of Figure 5 on a larger scale with ~3'~S

parts in different positions~
As indicated in Figure 1, the centrifugal pump of the present invention includes an upright drive shaft 1 received within an upright housing 2 forming a reservoir for oil or other lubricantD The bottom of the reservoir is closed by conventional antifriction bearings 3 for the drive shaft and a conventional seal 4.
The bottom portion of housing 2 is bolted to a pump casing 5 having a downward opening cavity or bowl 6 receiving the pump impeller 7J Such impeller consists o: a cylindrical shroud disc or plate 8 projecting radially from the impeller hub 9 fixed to the drive shaft; the primary pumping vanes or blades 10 projecting downward from the shroud plate; and vanes or ribs 11 projecting upward from the upper face of the shroud plate opposite the primary pumping blades 10.
The top of the pump bowl 6 i5 closed by a conventional seal 12 encircliny the drive shaft 1 7 and the bottom of the pump bowl is closed by an end plate 13 bolted to the bottom of the pump casing and having inlet apertures 14 which, as best seen in Figure 2, are arcuate and concentric with the axis of rotation of the drive shaft and the impeller.
A disintegrator or booster propeller 15 having generally radially projecting~ diametrally opposed blades 16 and a streamlined, con~exly curved bottom cap 17 is fixed to the bottom end of drive shaft 1. Rotation of the drive shaft, such as by an electric motor, effects rotation of the booster propeller for propelling a slurry of liquid, usually ~3~8~

water, and suspended solids constituting up to about 25 percent by weight of the slurry upward into the pump bowl through the arcuate inlet apertures 14 where the slurry is accelerated circumferentially and outward to the pump outlet conduit 18. Such outlet conduit extends generally tangentially from the impeller in its plane of rotation and is connected to a discharge conduit 19 for conveying the pumped slurry to a desired location~
The slurry pumped can include mixtures of water and~ for example, earth or vegetable pulp~ ~ut the pump is particularly useful for pumping mixtures of water and animal ~aste such as manure~ Such sewage slurries usually contain fairly large chunks or lumps of solid, sometimes stringy material which, to be pumped effectively, must be chopped or otherwise comminuted into relatively small pieces. Commonly the pump will be located near the bottom of a sump so that the slurry must be pumped upward a substantial distance~ As a result, the pressure of the slurry at the pump outlet must be high, that is, the pump must operate at a high headO
One factor that has been found to be important in increasing the head of a centrifugal slurry pump is the specific design of ~he disintegrator or booster propeller 15. The preferred design shown in Figures 2, 3 and 4 incorporates two generally radially extending, diametrally c>pposed blades 16 which, as shown in Figure 2, are of substantially uniform circumferelltial width from their roots to their tips~ As best seen in Figures 3 and 4, the leading edge ~0 of each blade is thin for ~3~

chopping or comminuting chunks or lumps of solid material in the slurry passing to the pump inlet.
While the root portions of the blades project substantially radially from the propeller hub~ the outer end portions of the blades are curved slightly rearward in the plane of rotation so that hard chunks or lumps of solid material will be impelled outward so as not to clog the pump inletO
The transverse section of Figure 4 illustrates the preferred cross-sectional shape for each propeller blade 16 throughout at least the major portion of its length. Its trailing side 21 i~
concave generally about an axis substantially parallel to the axis of rotation. For any transverse cross section an upright element of the trailing side 21 is substantially linear~ preferably substantially parallel to the axis of rotation. Also for any transverse cross section, preferably a laterally extending element of the lower side 22 of the blade is substantially linear and lies in a plane substantially perpendicular to the prop0ller axis; and for any transverse cross section preferably a laterally extending element of the upper, slurry-propelling side 23 of the blade also is substantially linear or only slightly concavely curved and is inclined upward from the leading edge 20 of the blade to the upper edge 24 of the trailing side 21, Accordingly~ throughout at least the major portion of its radial extent the blade is of generally triangular cross section, andl more specifically; of generally right triangular cross section~

In side elevation~ as shown in Figure 1, each blade 16 also is suhstantially triangular, the lower edge o the blade, def:ined by its cutting edge 20, appearing substantially :Li.near and inclined upward from the root of the blade to its tip, and the upper edge 24 of the blade, defined by the junction of the trailing side 21 and the upper surface 23t appearing substantially linear and lying in a plane substantially perpendicular to the axis of rotationO
Accordingly, each blade is tapered in axial extent substantially uniformly from its root to its tip.
As seen in Figure 3, at the tip of a blade 16 the angle of the upper surface 23 to a radial plane is sharply acute. Progressi.ng inward, the angle increases uniformly to the root of the blade and, since the blade is of substantially uniform circumferential width throughout its length, the propelling force generated by a rotating propeller blade is substantially uniform from the tip of the blade to its root because of the greater tip speed of the blade.
While each feature of the booster propeller is considered important, experiments have shown that of almost primary importance is that the blade be tapered in thickness from its trailing side 21 to its leading edge 20 and that the upright elements of the blade trailing side be substantially linear and, preferably, substantially parallel to the axis of rotation. Propellers substantially identical to the propeller shown in the drawings but having blades with convexly rounded trailin~ s.ides were much less effective in boosting the head of a centrifu~al pump.

.~

a The head-increasing tendency of the propeller also is aided by locating it at the entrance to or substantially within an outwardly flared funnel 28 which can conveniently be formed as a recess in the pump end plate 13 leading to the arcuate inlet apertures 14. The sides of the funnel flare outward at an angle of about 45 degrees relative to the axis of rotation, and the axial depth of the funnel should be at least equal to the maximum axial extent of a blade 16 of the booster propeller 15~ Such depth is about 10% to 15% of the diameter of the end plate. The maximum radius of the funnel should be at least about one and one-half times the radial extent of a blade 16~ Slurry at the radially outer margin of the end plate is accelerated smoothly through the funnel toward the current generated by the booster propeller.
Preferably the tips of the propeller blades extend to or sli~htly beyond the radially outer edges 27 of the arcuate inlet apertures which are faired by being rounded to assure a smooth flow into the pump.
Similarly the radially inner edges 27' of the inlet apertures are rounded for smooth flow of slurry into the pump.
While it is preferred that the propeller be located at the entrance to or substantially within the end plate funnel 28; it also is preferred that the propeller be spaced downward from the inlet apertures a distance suffici~nt that it will not interfere with the slicing effectiveness of the impeller blades 10 and entry of slurry and small particles into the pump casing past the propeller. In the embodiment shown in the drawings r a cylindrical spacer 25 spaces the IV

~341~

propeller downward from the flat inner portion of the end plate a distance only slightly less than the radial width of an inlet apertureO The lower portion of such spacer has a bevel 26 guiding the slurry toward the rounded radially inner edges 27' of the inlet apertures 14.
For assuring a compact design, the apertured end plate 13 is received within the pump bowl and has a bottom annular flange 29 enabling the end plate to be bolted to the upright sides of the pump casing 5.
As shown in Figure 6, the primary advantage of recessing the end plate into the pump bowl is that the planar upper surface 30 of the end plate can be located flush with the lower side 31 of the pump outlet conduit 18 which is integral with the pump casing 5~ In prior pumps, such as the pump of U.S.
patent NoO 3~973~866/ an end plate extends across the lower edge of a pump casing having an integral outlet conduit~ so that a substantial turbulence-promoting step occurs in the area of the entrance to such conduit~
To minimize backflow of high-pressure slurry in the pump casing 5 out the inlet apertures 14 r such apertures are located as close to the center of the impeller as possible. The radially outer edges of the inlet apertures are positioned approximately mid~ay between the axis of rotatlon and the radially outer tips of the primary pumping impeller blades 10~
Preferably at least the major portion of the inlet aperture area is located within a circle having a radius one-half the radius of the circle defined by th rotating impeller blades~

_ 1 1 ~

The specific design of the impeller also assures a high head and effective slicing action of chunks or lumps of solid material in the slurry being pumped. As best seen in Figures 5, 6 and 7 9 three primary pumping blades 10 ar provided projecting downward from khe shroud plate 8 t each of substantially constant cixcum erential width throughout its length~ Each blade is at least several times longer than its axial height and projects first generally tangentially from the impeller hub 9 and then is curved spirally rearward in the plane of rotation.
As best seen in Figure 7, the lower leading edge 33 of each blade is sharpened and i5 in close slicing relationship to the upper side 30 of the pump casing end plate 13. For this pwrpose the leading arcuate sides 34 of the end plate inlet apertures are beveled to a rearward facing sharpened edge 34' for close slicing contact with the leading sharpened edges 33 of the blades.
Whereas prior centrifugal slurry pumps having used blades that project generally radially in the area of the inlet apertures for abrupt chopping of chunks or lumps of solid material in the slurry~ the blades of the present invention are angled rearward in the area of the inlet apertures at a substantial angle relative to a radius, preferably at least 45. As best seen in Figure 2g the apparent movement of a blade as it approaches a sharpened leading edge 34' of an inlet aperture 14 is both forward and radially outward or effecting an angular slicing action, as opposed to an ~brupt chopping action, of chunks or lump5 of solid material in the slurry~
, ~

~3~5 So that the primary impeller vanes 10 do not themselves interfere with ent:rance of slurry through the inlet apertures, it i5 preferred ~hat the oircumferential width of the blades be as small as possible at their lower sides 35, preferably no greater than one-half the radial width of the inlet apertures~ As best seen in Figure 7, however 7 the upper portions of the leading sides 32 and the trailing sides 36 of blades should be faired gently into the shroud plate by fillets extending from about the axial center of each blade for smooth change o~
flow direction of the slurry from a ~enerally axial direction to accelerated movement in the plane of rotation~ As a result of the fairing, the blades are tapered in circumferential width from their roots to their tips such that the circumferential width of each blade at its tip is no greater than about one-half the circumferential width of the blade at its root. In combination with the fairing of the leading side 32 of the blade into the shroud plate, the forward curved lower tip poxtion of the blade leading to the sharpened cutting edge 33 forms a substantial forward opening cup that is swept spirally rearward in the plane of rotation for effective but smooth acceleration of the slurry circumferentially forward and outward toward the pump outlet. As shown in Figure 7~ the fairing of the trai1ing side 36 of the blade into the shroud plate 8 is more gradual than the fairing of the leading side 32 into such plate, that is, the radius of curvature of the fillet formed at the upp~r portion of the trailing side is greater than the radius of curvature of the fillet formed at the upper portion o~ the leading side.

~13-~;~93~

The axially short ribs or vanes 11 projecting upward from the shroud plate are provided primarily to protect the seal 12 rather than to assist in pumping the sl.urry~ Such vanes are substantially shorter than the primary pumping vanes 10, and more upper vanes 11 are provided at closer spacing. Rather than being volute or curved rearward in the plane of rotation~ such upper vanes 11 are substantially straight though angled rearward as to be generally tangential to the periphery of the drive shaft 10 As with the lower primary pumping blades 10~ such upper vanes 11 are faired into the shroud plate by fillets extending from at least about their axial centers as shown in Figure 7.
The overall design of the upper vanes 11 results in development of higher pressure at the periphery and above the shroud plate 8 than below it so that there is some suction above the plate away from the seal 120 Accordingly, lubricant from the 2G reservoir in housing 2 tends to be drawn through the bearings 3, the seal 4 and the seal 12, assuring longer life than if a positive pressure were exerted above the shroud plate toward the seals which could force slu.rry through the seals and bea.rings into the lubricant housing~ In addition, seal failure is quickly and accurately detected by a rapid decrease in the level of lubricant in the reservoir formed by the housing.
A final factor affecting the head of th~
pump is the design of the pump casing 5. As shown in ~3~8~
Figure 5, rather than being spiraled or volute throughout its circumference~ that is, rather than having a progressively increasing radial extent between the casing and the radially outer ends of the pump blades in the direction of rotation, such casing is semicylindrical and semivolute. Beginning at the outlet conduit 18 and rnoving opposite the direction of rotation, for about one-half the circumference of the impeller~ the casing spirals inward toward the shroud plate, and for the final one-half of its circumference the casing closely encircles the shroud plate providing a semicylindrical zone. Since slurry cannot escape outward in the semicylindrical zone, pressure of the slurry increases substantially in this zone before the slurry can escape circumferentially toward the outlet conduit and, as a result, the head of the pump is substantially increased.

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Claims (3)

The embodiments of the invention in which an exclusive property or privilege is claimed are defined as follows:

1. In a centrifugal pump, the improvement comprising the combination of a pump casing forming a bowl of generally circular cross section and having a substantially closed end, an open end and a circumferential outlet, an impeller received in said bowl, rotatable therein and having pumping vanes projecting toward said open end of said casing, drive shaft means extending generally axially through said substantially closed end of said casing and carrying said impeller, an end plate recessed into and closely fitted in said open end of said casing so that the inner face of said end plate adjacent to said impeller is flush with the adjacent face of said circumferential outlet, the outer face of said end plate forming an outwardly flared funnel and said end plate having an inlet at the base of said funnel for intake of material into said casing, a booster propeller coaxial with said impeller and located outside said casing, and spacer means journaled in said end plate at the base of said funnel, interconnecting said impeller and said booster propeller for conjoint rotation and positioning said booster propeller at approximately the entrance of said funnel.

2. In a pump as defined in claim 1, the end plate inlet including a plurality of separate arcuate inlet apertures, and the impeller vanes having edges in close slicing relationship with edges of said arcuate inlet apertures.

3. In a pump as defined in claim 2 , the outer margins of the arcuate inlet apertures being rounded for smooth flow of material into thP pump casing.