Abstract:
An improved low specific speed pump is disclosed, which provides for greater consistency of pump operating efficiencies obtainable by pumps of any given group of like size pumps. In the present pump, the internal dimensions of the pump chamber and discharge passage are enlarged to provide for a reduction in flow velocities therewithin compared to a conventional pump of a given design flow capacity and a controlled size restrictor is arranged adjacent the pump discharge in order to reduce the resultant increase in flow capacity to such given design value.

Description:
BACKGROUND OF THE INVENTION 
     The invention relates to an improvement in low specific speed centrifugal pumps. 
     It is well known that frictional and mixing losses limit the efficiency of centrifugal pumps and that such losses decrease and increase, respectively, as specific speed increases. Specific speed is a design characteristic number designated as Ns and equals ##EQU1## wherein Ω is flow rate in gallons per minute, rpm is pump impeller revolutions per minute and H is the developed head of a pump in feet. For pumps having relatively low specific speeds, i.e., below the range of about 600-700, frictional losses exceed mixing losses and have a substantial effect on pump performance. 
     Low specific speed pumps provided with cast metal casings are known to be subject to substantial variations from design pump performance, due to substantial variations in frictional losses resulting from minor variations in size of the pump chamber and the surface finish thereof commonly encountered with metal castings. While it is possible to machine or hand work the internal surfaces of such pumps, with a view towards obtaining greater uniformity in size and surface finish in order to decrease the overall variations in efficiency, to do so adds substantially to manufacturing costs. 
     SUMMARY OF THE INVENTION 
     The present invention is specifically directed to the provision of low specific speed centrifugal pumps having relatively uniform performance characteristics. 
     In accordance with the present invention, the casing of an otherwise conventional low specific speed centrifugal pump is modified by enlarging its pump chamber and discharge passage, as compared to a like pump of a given output flow rate, and a restrictor is placed adjacent the outlet end of the discharge passage for purposes of throttling the flow output from the pump to a value equal to such given flow rate. The interior of the pump casing is enlarged as required to reduce the flow velocity of pump fluid therewithin to an extent such that minor variations in size and surface finish occasion substantially less frictiion loss than encountered in a comparable pump having the same discharge flow rate. The required percentage increase in the size of the pump interior will tend to increase, as specific speed decreases, in that interior flow velocities, and thus losses due to frictional effects tend to increase as the value of specific speed decreases. 
     In accordance with the present invention, the restrictor is defined by forming an accurately sized flow opening in a constriction formed adjacent the outlet end of the discharge passage, as an incident to casting of the pump casing. By selection of the size of drill used in forming the restrictor flow opening, a given size of pump may be modified to provide a family of pumps having different performance characteristics. 
    
    
     DRAWINGS 
     The nature and mode of operation of the present invention will now be more fully described in the following detailed description taken with the accompanying drawings wherein: 
     FIG. 1 is a sectional view taken through a conventional centerline discharge, relatively small size and relatively low specific speed centrifugal pump modified in accordance with the present invention; 
     FIG. 2 is a sectional view taken generally along the line 2--2 in FIG. 1. 
     FIG. 3 is a sectional view taken generally along the line 3--3 in FIG. 1; and 
     FIG. 4 is a graph generally comparing friction and mixing losses encountered with a pump modified in accordance with the present invention and a conventional pump of like performance characteristics. 
    
    
     DETAILED DESCRIPTION 
     Reference is first made to FIG. 1, wherein 10 designates a centerline discharge, low specific speed centrifugal pump having a casing 12 formed to define a pump chamber 14, an inlet opening 16 connected to a fluid supply, not shown, and a discharge passage 18 having an outlet end 20 connected to a discharge pipe 22; and an impeller 24 mounted for rotation within pump chamber 14 for purposes of pumping fluid between inlet opening 16 and outlet end 20. Pump chamber 14 is shown as being of the volute type, wherein the distance between its radial, outer boundary surface 26 and the rotational axis 28 of impeller 24 progressively increases in the direction of rotation of the impeller from adjacent a cut-water 30 to an inlet end or throat area 32 of discharge passage 18. However, the present invention is also adpated for use in pumps of the type in which outer boundary surface 26 is disposed essentially concentrically of axis 28. Further, the present invention is equally adapted for use with pumps having closed or open impellers. 
     The full line showing in FIGS. 1-3 depicts a pump formed in accordance with the present invention, which differs from a known pump having the same operating characteristics principally with respect to the internal size and shape of its pump chamber and discharge passage. For purposes of comparison, broken lines 26&#39; are used in FIGS. 1 and 3 to indicate the placement of the outer boundary wall of the known pump. 
     By referring to FIG. 4, it will be understood that for known low specific speed pumps, i.e., pumps having specific speeds below about 600-700, loss in efficiency is primarily due to losses occasioned by frictional effects, although mixing losses tend to become a progressively greater loss factor as the specific speed of the pump increases. It will also be understood that frictional losses for pumps of any given type and size, which are provided with cast metal casings, are not constant, due to minor variations in size and surface finish of the chamber and throat areas of a pump typically encountered in such castings. As by way of example, for the case of 11/2×2-9 size pumps (the numerals designating discharge opening diameter, inlet opening diameter and nominal impeller diameter in inches) manufactured by Goulds Pumps, Incorporated of Seneca Falls, N.Y., individual pumps of a group of ten such pumps, will typically have actual performance efficiencies of between about 45 percent and 50 percent, thus creating an actual difference in efficiency between pumps of such group of about 10 percent. While the design efficiencies of a pump will vary directly with its discharge flow rate and/or specific speed, there still remains a range of differences in actual efficiencies obtained by pumps within a group of like size pumps. In that this variation is not acceptable, it is normally necessary to perform hand work on one or more of the pumps in order for them to meet desired minimum performance standards. 
     Again referring to FIG. 1, it will be understood that in accordance with the present invention, the interior of the casing of a given size of pump is cast oversize, as compared to a like sized known pump, so as to achieve a decrease in the velocity of fluid within pump chamber 14 and through the throat area of discharge passage 18. It has been found that for the previously mentioned 11/2×2-9 size pump, an increase of the size of pump chamber 14 effected by arranging points along boundary surface 26 at a distance from rotational axis 28, which are more than about 15 percent to 20 percent greater than the distance measured between 26&#39; and such rotational axis, while maintaining the same axial dimension or width of the pump chamber and discharge passage, there may be achieved about a 15 percent decrease in flow velocity within the pump chamber, which is sufficient to substantially diminish frictional losses due to minor variations in size and surface finish normally found in casings of this size pump. 
     It is, of course, possible to further enlarge pump chamber 14 of any given size pump to achieve reductions in flow velocities of 50 percent or more, but there are certain practical limitations including the size of discharge pipe 22 and the cost of casting a casing having an exterior size sufficient to provide a safe casing wall thickness, as measured outwardly of boundary surface 26. In general, the relative percentage increase of the size of the interior of a pump will be required to increase as the specific speed of such pump decreases. Thus, for example, percentage increases in the range of 30 percent to 40 percent are contemplated as being required for pumps having specific speeds below about 450. This is due to the fact that interior flow velocities tend to increase as specific speed decreases. As by way of example, pumps having specific speeds of 70 and 450 may have internal velocities on the order of about 75 feet/second and 125 feet/second, respectively. It is to be noted that the position of cut-water 30 and the radial distance between such cut-water and the periphery of impeller 24 or its rotational axis 28 remain unchanged from that of an unmodified or known pump. 
     As will be apparent, simply increasing the size of pump chamber 14 of any given size pump would serve to produce a much larger pump discharge flow rate than desired. Accordingly, in the present invention, a restrictor 34 is placed adjacent outlet end 20 of discharge passage 18 for purposes of throttling the output of the pump to a value equal to the design flow rate of the unmodified pump, i.e., the design flow rate resulting from a pump having a chamber and discharge passage boundary wall 26&#39; determined by standard design criteria. Restrictor 34 is preferably formed by integrally casting a constriction adjacent the outlet end of discharge passage 18 and then machining an accurately sized flow opening or bore 36 therethrough, as by performing drilling and reaming operations. The constriction, as formed, may completely close the discharge passage, but is preferably formed with a small pilot hole to facilitate the machining operation. Frictional loss occasioned by flow opening 36 is relatively small, due to its relatively smooth machined surface and short axial length. The following examples of low specific speed pumps formed in accordance with the present invention and prior practice are given as by way of illustration: 
     
         __________________________________________________________________________             Prior  New Design Design        Area of             Area of                  Spec.Pump   Area of        Casing             Casing                  Speed                      Q   ImpellerSize   Restrictor        Throat             Throat                  (Ns)                      (gpm)                          type__________________________________________________________________________11/2 × 2-7  .29   .35  .22  533  55 closed11/2 × 2-9  .60   .61  .39  508 120 closed11/2 × 3-11  .74   .88  .57  511 200 closed 1 × 2-10  .57   .60  .40  466 180 open 2 × 3-13  1.23  1.66 .81  500 350 closed__________________________________________________________________________ 
    
     It will be understood that pump size per se is not limited on this present invention, as long as the pump has a relatively low specific speed at which sufficient variations in frictional losses between like sized pumps warrant practice of the present invention. 
     By increasing the size of the pump chamber and discharge passage and employing an accurately sized flow opening, as opposed to throat area 32 as in conventional pumps, to limit the flow rate to a desired value, two advantages are obtained; namely, the overall loss due to friction is substantially reduced and the variation in frictional losses within a group of like pumps is substantially diminished, as indicated in FIG. 4. On the other hand, an obvious disadvantage of increasing the size of the pump chamber is that mixing losses substantially increase, also as indicated in FIG. 4. However, it has been found that the net effect of these decreased and increased losses due to friction and mixing, respectively, is advantageous for the case of low specific speed pumps. In this respect, it has been determined that for the type of pump under consideration, the reduction in frictional loss and the increase in mixing loss tend to balance each other with some possible small increase in overall pump efficiency being noted. However, of more importance is the fact that the variation in total loss between like pumps is substantially decreased. Thus, for the case of the 11/2× 2-9 size pump mentioned above, conventionally formed pumps will have actual efficiencies typically varying between 45 percent and 50 percent within a given group of such pumps, whereas like pumps formed in accordance with the present invention will have actual efficiencies varying between 49 percent and 50 percent, with some pumps appearing to even slightly exceed the design efficiency of 50 percent. The operating characteristics of the improved and unmodified or known pumps will otherwise be essentially the same. Thus, the primary advantage of the present invention, is that pumps having efficiencies lying within a relatively small range of acceptable manufacturing tolerances may be consistently manufactured without resorting to hand machining of individual pumps to bring same within acceptable tolerances. 
     A further advantage flowing from the practice of the present invention is that a given size pump may be modified to provide a family of pumps having different characteristics by merely varying the diameter of the restrictor flow opening. Thus, as by way of example, the 11/2×2-9 size pump may be used to create a family of pumps having for instance maximum flow rates of about 120 gpm, 110 gpm and 70 gpm by providing restrictor flow openings of 7/8 inch, 13/16 inch and 11/16 inch, respectively. Of course, the actual efficiency of the 110 gpm and 70 gpm pumps will be less than the actual efficiency of the 120 gpm pump, but the percentage of efficiency variation within any group of such smaller output pumps will remain sufficiently small, so as to permit consistent manufacture thereof without hand working of individual pumps to bring same within acceptable tolerances. 
     While in accordance with the presently preferred form of the invention, the internal size of a pump is changed by increasing only its radial dimension, it is contemplated that an increase in size may be obtained, if desired, by increasing both the radial and axial dimensions or only the axial dimension of the pump chamber and discharge passage.