Centrifugal pump for a gas turbine engine

Information

  • Patent Grant
  • 6361270
  • Patent Number
    6,361,270
  • Date Filed
    Friday, September 1, 2000
    23 years ago
  • Date Issued
    Tuesday, March 26, 2002
    22 years ago
Abstract
A centrifugal pump for a gas turbine engine, including a housing having a fluid inlet port for receiving fluid at an initial pressure and an interior chamber defining a central axis. An impeller disk disposed within the interior chamber of the housing and mounted for rotation about the central axis. The impeller disk defines first and second inlet areas and has a plurality of circumferentially spaced apart channels formed therein which extend from the inlet areas for conducting fluid from the inlet areas in a radially outward direction upon rotation of the impeller disk so as to increase the pressure of the fluid. A first collector is formed by the housing for receiving the fluid from the first inlet area via the channels at a first elevated pressure relative to the initial pressure and a second collector is formed by the housing for receiving fluid from the second inlet area via the channels at a second elevated pressure relative to the first elevated pressure. A cross-over conduit is formed by the housing for conducting fluid from the first collector to the second inlet area of the impeller disk and an outlet is formed by the housing for conducting fluid from the second collector.
Description




BACKGROUND OF THE INVENTION




1. Field of the Invention




The present disclosure relates to a centrifugal pump, and more particularly, to a low specific speed centrifugal pump for use in conjunction with a fuel metering unit for a gas turbine engine.




2. Background of the Disclosure




Pumps have been widely used and are well understood in the art. They are utilized in a variety of applications such as petroleum refining plants and combustion engines. In use, pumps increase the flow and/or pressure of a fluid within a system in order to adequately supply a device which requires fluid with an increased fluid flow and/or pressure.




The present disclosure involves booster pumps. The term “booster” is used to describe various applications. A “booster stage” may mean a separate secondary pump on the inlet of a primary pump to further increase the net positive suction head (hereinafter “NPSH”) to the inlet of the primary pump. Traditionally, one employed low specific speed centrifugal pumps as the “boost stage” of a fuel metering unit for small gas turbine engines. Such centrifugal pumps are typically low speed (e.g., 6,000-12,000 rpm) and low volumetric flow, yet the boost stage must produce a relatively high pressure rise (e.g., 200 psid). A “booster” may also refer to a suction device, such as an inducer, incorporated as part of a primary pump to improve its NPSH. Further, a secondary pump or impeller downstream and in series with the primary pump to increase discharge pressure is also called a “booster”.




Several systems have been developed to more efficiently and cost effectively energize a fluid pathway. For example, U.S. Pat. No. 5,779,440 to Stricker et al. discloses means for forming jet sheets upstream of an impeller. The device includes a recirculation chamber surrounding an impeller shroud for recirculating fluid back through the impeller. It is also common for pumps to have multiple impellers in series which move the same fluid, e.g., “multi-stage” pumps. Multistage pumps further increase the flow and pressure of fluid. U.S. Pat. No. 5,599,164 to Murray shows a multi-stage centrifugal pump assembly including primary and booster impellers, wherein the inlet of the secondary impeller is connected to the outlet of the primary impeller.




Despite their utility, there are disadvantages associated with these prior art systems. For example, multiple impellers increase cost, complexity and require additional drive mechanism horsepower. Additional complexity involves more costly maintenance creating an undesirably high cost of ownership. Prior art pumps are inefficient. Pump efficiency is the pump output in terms of liquid horsepower compared to the horsepower delivered to the drive shaft. Seal and windage loss decrease efficiency. Seal loss is the fluid leakage from higher pressurized areas to lower pressurized areas. Windage, the drop in efficiency due to impeller friction, is the predominant type of loss in many pumps. In particular, relatively large diameter impellers and relatively narrow width impeller blades which are necessary to achieve the desired performance increase windage which reduces efficiency. In addition, temperature increases for the fluid can occur as the fluid is pumped through the fluid. In many instances, such temperature increases are undesirable.




In view of the foregoing deficiencies, there is a need for a compact, lightweight, economical and reliable low specific speed centrifugal pump with improved efficiency, and which does not increase the temperature of the fluid pumped thereby.




SUMMARY OF THE INVENTION




The present invention provides a centrifugal pump for a gas turbine engine, including a housing having a fluid inlet port for receiving fluid at an initial pressure and an interior chamber defining a central axis. An impeller disk disposed within the interior chamber of the housing and mounted for rotation about the central axis. The impeller disk defines first and second inlet areas and has a plurality of circumferentially spaced apart channels formed therein which extend from the inlet areas for conducting fluid from the inlet areas in a radially outward direction upon rotation of the impeller disk so as to increase the pressure of the fluid. A first collector is formed by the housing for receiving the fluid from the first inlet area via the channels at a first elevated pressure relative to the initial pressure and a second collector is formed by the housing for receiving fluid from the second inlet area via the channels at a second elevated pressure relative to the first elevated pressure. A cross-over conduit is formed by the housing for conducting fluid from the first collector to the second inlet area of the impeller disk and an outlet is formed by the housing for conducting fluid from the second collector.




Preferably, the plurality of circumferentially spaced apart channels are bifurcated adjacent an outer diameter of the impeller and the impeller is configured in such a manner so that at least seventy percent of the circumferentially spaced apart channels are in fluid communication with the first and second inlet areas. In yet another embodiment, the first collector and the second collector are diametrically opposed from one another relative to the central axis of the housing.




In another embodiment, the housing further defines sealing lands with the impeller disk for sealingly isolating the first and second collectors. In another embodiment, the impeller disk may be shrouded, unshrouded or open. The plurality of circumferentially spaced apart channels are preferably adapted and configured to facilitate fluid communication between the first inlet area and the first collector, and between the second inlet area and the second collector.




Still another embodiment of the present invention includes a device which comprises an inducer, having a helical blade extending radially outward, rotatably mounted about the central axis of the housing for drawing fluid axially from the fluid inlet port to the first inlet area of the impeller disk.




And yet another embodiment of the present invention includes a housing with a partition within the interior chamber for isolating the first inlet area from the second inlet area. Preferably, the partition defines a third inlet area, the outlet conducts fluid from the second collector to the third inlet area and the housing defines a third collector outward of the impeller for receiving the fluid passed through the impeller from the third inlet area and a second outlet formed by the housing for conducting fluid from the third collector. It is also envisioned that a first elevated pressure outlet may be provided for conducting the fluid from the first collector to allow the centrifugal pump to supply the fluid at the first elevated pressure and the second elevated pressure.











BRIEF DESCRIPTION OF THE DRAWINGS




So that those having ordinary skill in the art to which the low speed specific centrifugal pump of which the subject invention appertains, reference may be had to the accompanying drawings wherein:





FIG. 1

is a perspective view of a low specific speed centrifugal pump constructed in accordance with a preferred embodiment of the subject invention, with a housing of the pump cut-away to reveal an inducer and an impeller therein; and





FIG. 2

is another perspective view of the low specific speed centrifugal pump of

FIG. 1

, with the housing of the pump cut-away to reveal a sealing landing;





FIG. 3

is a cross-sectional view of the low specific speed centrifugal pump of

FIG. 1

;





FIG. 4

is another perspective view of the low specific speed centrifugal pump of

FIG. 1

, illustrating the pump in a fully assembled condition; and





FIG. 5

is a schematic view of a multiple cross-over conduit pump constructed in accordance with a preferred embodiment of the subject invention.











DETAILED DESCRIPTION OF THE DISCLOSURE




The present invention relates to an improved boost pump for increasing the pressure of a fluid. The system is particularly applicable to supplying fluid to a fuel metering unit for use with a small gas turbine engine, although the system and method may be utilized in many applications, such as low specific speed centrifugal pumps for use as a “boost stage” with large gas turbine engines, as would be readily appreciated by those skilled in the art.




The present invention overcomes many problems of the prior art associated with pumps. The advantages, and other features of the system disclosed herein, will become more readily apparent to those having ordinary skill in the art from the following detailed description of certain preferred embodiments taken in conjunction with the drawings which set forth representative embodiments of the present invention and wherein like reference numerals identify similar structural elements.




Referring to

FIGS. 1 and 2

, there is illustrated a low specific speed centrifugal pump


10


with the housing cut away for ease of illustration. Centrifugal pump


10


is intended for use as a secondary pump to increase the initial fluid pressure at the main pump, e.g., “a boost stage” for a fuel metering system of a gas turbine engine (not shown). Centrifugal pump


10


includes a generally cylindrical housing


12


having an impeller casing


14


configured to surround a disk-like impeller


16


, and a substantially funnel-shaped inducer casing


18


for surrounding an inducer


20


. Inducer


20


and impeller


16


are mounted for rotation about a common axis on a drive shaft


52


in the direction indicated by the arrow designated


70


. In a preferred embodiment, when inducer


20


and impeller


16


are rotating, fluid is drawn into pump


10


and the pressure of the fluid is elevated to 100 to 200 psid. Drive shaft


52


extends through a bore in housing


12


to connect to a drive motor (not shown) for supplying torque to the drive shaft


52


. Drive shaft


52


typically rotates at a low speed (e.g., within the range of 6,000 to 12,000 rpm).




Still referring to

FIGS. 1 and 2

, impeller casing


14


defines first and second collector areas


30


and


32


, respectively. The first and second collector areas


30


and


32


extend outside the outer diameter of impeller


16


. In a preferred embodiment, the first and second collector areas


30


and


32


are diametrically opposed, however they may be arranged in a different manner. Inducer casing


18


extends from impeller casing


14


, and defines pump inlet


40


and top end


38


. During operation, fluid enters pump


10


via pump inlet


40


. Adjacent to pump inlet


40


, inducer


20


includes blades


54


which extend radially outward. When rotating on drive shaft


52


, inducer


20


reduces the NPSH requirement of pump


10


and charge impeller


16


with fluid at sufficient pressure. In an alternative embodiment of the subject invention, the pump does not include an inducer. Therefore, the incoming fluid is conducted towards impeller


16


under its own pressure.




Still referring to

FIGS. 1 and 2

, sealing land


42


is operatively associated with inducer casing


18


. Sealing land


42


includes upstanding helical flange


43


which surrounds inducer


20


to divide an interior of inducer casing


18


into a first portion


44


adjacent top end


38


, and a second portion


46


adjacent impeller


16


. Upstanding helical flange


43


directs fluid from pump inlet


40


to first inlet area


22


. Sealing land


42


also includes shoulders


26


and


28


located within the inner diameter


56


of impeller


16


for defining the first and second inlet areas


22


and


24


. The radially outwardly facing portions of shoulders


26


and


28


form non-contacting seals with inner diameter


56


of impeller


16


. Similarly, the radially inwardly facing portions of shoulders


26


and


28


form non-contacting seals with inducer


20


. As a result, shoulders


26


and


28


partition the first and second inlet areas


22


and


24


to substantially prevent leakage therebetween.




Housing


12


also includes a cross-over conduit


48


providing fluid communication between first collector area


30


and second portion


46


of inducer casing


18


. Cross-over conduit


48


allows fluid to pass from first collector area


30


to second inlet area


24


in the direction indicated by the arrow designated


72


. Upstanding helical flange


43


and shoulders


26


and


28


combine with one another to prevent the fluid exiting crossover conduit


48


from leaking into first inlet area


22


. Pump outlet conduit


50


conducts fluid out from second collector area


32


of impeller casing


14


.




Referring to

FIG. 3

, impeller


16


includes a plurality of major radial vanes


60


(


a


)-(


n


) and minor radial vanes


61


(


a


)-(


n


). Major radial vanes


60


(


a


)-(


n


) and minor radial vanes


61


(


a


)-(


n


) define a plurality of corresponding bifurcated flow channels


64


(


a


)-(


n


). For simplicity, not all of major radial vanes


60


(


a


)-(


n


), minor radial vanes


61


(


a


)-(


n


) and bifurcated flow channels


64


(


a


)-(


n


) are labeled on the figures. The variable “n” is used for illustration and should not be considered a limitation in any way to the number of vanes or channels present in impeller


16


. Preferably, on the side opposing inducer


20


, impeller


16


is uniform thereby corresponding to the class of impellers known as unshrouded. In another embodiment, the impeller is comprised of one uniform disc mounted as a backing for a disc with a plurality of vanes. However, it is also envisioned that an impeller having no disc (e.g., an open impeller), having a disc on each side (e.g., a shrouded impeller) or having a disk with channels on both sides (e.g., vertical stage) could be provided. Each different type of impeller may be thin-channel as illustrated in the figures or other conventional type such as a vane impeller.




With continuing reference to

FIG. 3

, channels


64


(


a


)-(


n


) of impeller


16


provide fluid communication between first inlet area


22


and first collector area


30


of impeller casing


14


, and between second inlet area


24


and second collector area


32


. The plurality of major radial vanes


60


(


a


)-(


n


) and minor radial vanes


61


(


a


)-(


n


) are arranged and configured such that as impeller


16


rotates about the shaft


52


, the inner ends of each channel


64


(


a


)-(


n


) are in fluid communication with first inlet area


22


, and the corresponding outer ends are in fluid communication with first outlet area


30


. Similarly, when inner ends of each channel


64


(


a


)-(


n


) are in fluid communication with second inlet area


24


, corresponding outer ends are in fluid communication with second outlet area


32


. Preferably, at least 70% of channels


64


(


a


)-(


n


) are in fluid communication with an inlet area at all times. First and second collector areas


30


and


32


are separated by inwardly facing sealing lands


34


and


36


to prevent leakage of fluid therebetween. In particular, the outer diameter of impeller


16


forms a non-contacting seal with sealing lands


34


and


36


of impeller casing


14


.




Referring to

FIG. 4

, there is illustrated a perspective view of an assembled low specific speed centrifugal pump


10


constructed in accordance with the present disclosure. It is envisioned and well within the scope of the subject disclosure that housing


12


, impeller


16


and inducer


20


may be of monolithic construction. Alternatively, funnel shaped inducer casing


18


may be threadably engaged to disk shaped portion


14


and cross-over conduit


48


may press fit to inducer casing


18


. Further, disk shaped portion


14


may be formed from component pieces that are threadably engaged or press fit to one another. Similarly, collar


38


for sealingly engaging a fluid supply may attach to inducer casing


18


by press fit or threads. As such, it will be appreciated by those skilled in the art that various structures and methods may be used to construct housing


12


without deviating from the scope or spirit of the invention.




In operation, torque is supplied to drive shaft


52


of pump


10


by a drive motor (not shown). Drive shaft


52


rotates inducer


20


and impeller


16


about a common axis. A fluid, e.g., a liquid fuel, is introduced through pump inlet


40


and pumped axially inward by inducer


20


to first portion


44


of inducer casing


18


. Inducer


20


and helical flange


43


direct the fluid through first portion


44


into first inlet area


22


where the only exit path is into the channels


64


(


a


)-(


n


) of rotating impeller


16


. Upon entering channels


64


(


a


)-(


n


), the fluid is directed radially outwardly from the first inlet area


22


and accumulated within the first collector area


30


of impeller casing


14


. Directing the fluid radially outward increases the fluid pressure. Within first collector area


30


, the pressure of the fluid is increased approximately 50% of the total pressure increase provided by centrifugal pump


10


.




Cross-over conduit


48


diffuses the flow of the partially pressurized fluid and conducts the fluid from first collector area


30


to the second portion


46


of inducer casing


18


where it is directed to second inlet area


24


. From the second inlet area


24


, the fluid is again directed radially outwardly through channels


64


(


a


)-(


n


) of rotating impeller


16


to further increase the fluid pressure. However, here, the fluid passes from the second inlet area


24


to second collector area


32


. When the fluid reaches the second outlet area


32


, centrifugal pump


10


has increased the pressure of the fluid to the desired level. From there, pump outlet conduit


50


conducts the fully pressurized fluid from second collector area


32


to another device in the fluid path, such as, into the main pump and fuel metering means of a gas turbine engine.




Theory indicates that the centrifugal pump


10


of the present disclosure results in an impeller


16


having a diameter that is about thirty percent less than the diameter of an impeller of presently existing pumps producing similar pressure rises. Thus, windage loss is substantially reduced. Pump


10


also results in approximately twice the overall efficiency of existing pumps producing a similar pressure rise, while producing half the temperature rise in the fluid being pumped.




In another embodiment, low specific speed centrifugal pump may include more than one cross-over conduit. It is envisioned that a pump according to the present disclosure can have multiple cross-over conduits and an impeller casing with a corresponding number of inlet areas and collector areas. The total number of cross-over conduits employed is limited only by geometric considerations and proper pump design practice, as will be appreciated by those skilled in the art.




For example, referring to

FIG. 5

, a pump


110


with two cross-over conduits in accordance with the subject invention is illustrated schematically. Channels


164


(


a


)-(


n


) of impeller


116


provide fluid communication between first inlet area


122


and first collector area


130


of impeller casing


114


, between second inlet area


124


and second collector area


132


, and between third inlet area


126


and third collector area


134


. In particular, the plurality of major radial vanes


160


(


a


)-(


n


) and minor radial vanes


161


(


a


)-(


n


) are arranged and configured such that as impeller


116


rotates, the inner ends of each of channel


164


(


a


)-(


n


) are in fluid communication with first inlet area


122


, and the corresponding outer ends are in fluid communication with first outlet area


130


. Similarly, when inside ends of each of channels


164


(


a


)-(


n


) are in fluid communication with second inlet area


124


, corresponding outer ends are in fluid communication with second outlet area


132


. Further similarly, when inside ends of each of channels


164


(


a


)-(


n


) are in fluid communication with third inlet area


126


, corresponding outer ends are in fluid communication with third outlet area


134


. First, second and third collector areas


130


,


132


and


134


are separated by inwardly facing sealing lands


137


,


138


and


139


to prevent leakage of fluid therebetween. In particular, the outer diameter of impeller


116


forms a non-contacting seal with sealing lands


137


,


138


and


139


of impeller casing


114


. Cross-over conduit


148


conducts the fluid from the first collector area


130


to the second inlet area


124


of impeller casing


114


. Similarly, cross-over conduit


149


conducts the fluid from the second collector area


132


to the third inlet area


126


of impeller casing


114


. Outlet conduit


150


conducts the fully pressurized fluid from the third collector area


134


.




In yet another embodiment, a pump according to the present disclosure may be provided with a vertical stage impeller wherein the outlet conduit would direct the fluid to an inlet area on the opposite side of the impeller where the fluid would be passed through the impeller again for further pressurization. The disk of the vertical stage impeller sealingly isolates the top and bottom sides of the impeller. Additionally, the opposite side may include additional conduits to route the fluid to and from multiple inlet areas and collectors to highly pressurize the fluid.




In still another embodiment, a pump according to the present disclosure may be provided without an inducer or inducer casing. In such an embodiment, pump inlet would connect directly to the first inlet area and the cross-over conduit would connect directly to the second inlet area. Additionally, a pump according to the present disclosure may be provided with an outlet conduit in fluid communication with the first collector area. As a result, the pump would provide two fluid streams at different pressures.




Although, the subject disclosure relates to boost stages, those skilled in the art will readily apply the disclosure to use in a main pump. Those skilled in the art will also appreciate that the subject disclosure is equally applicable to compressors. Such a compressor may have application in turbines, automotive air conditioners, refrigeration units and the like.




While the presently disclosed low specific speed centrifugal pump has been described in connection with a preferred embodiment, such is intended to be exemplary only and not definitive and it will be appreciated by those skilled in the art that many modifications, changes and substitutions may be made thereto without departing from the spirit or scope of the invention as defined by the appended claims.



Claims
  • 1. A centrifugal turbo machine for increasing the pressure of a fluid, comprising:a) a housing having a fluid inlet port for receiving fluid at an initial pressure and an interior chamber defining a central axis; b) an impeller disk disposed within the interior chamber of the housing and mounted for rotation about the central axis, the impeller disk defining first and second inlet areas and having opposed, upper and lower disk surfaces, the upper surface having a plurality of circumferentially spaced apart channels formed therein for conducting fluid from the inlet areas in a radially outward direction upon rotation of the impeller disk so as to increase fluid pressure, wherein the plurality of circumferentially spaced apart channels are defined between the upper and lower disk surfaces; c) a first collector formed by the housing for receiving the fluid from the first inlet area via the channels at a first elevated pressure relative to the initial pressure; d) a second collector formed by the housing for receiving fluid from the second inlet area via the channels at a second elevated pressure relative to the first elevated pressure; e) a cross-over conduit formed by the housing for conducting fluid from the first collector to the second inlet area of the impeller disk; and f) an outlet formed by the housing for conducting fluid from the second collector.
  • 2. A centrifugal turbo machine as recited in claim 1, wherein the housing further defines sealing lands with the impeller disk for sealingly isolating the first and second collectors.
  • 3. A centrifugal turbo machine as recited in claim 1, wherein the impeller disk is selected from the group of impellers consisting of shrouded, unshrouded and open.
  • 4. A centrifugal turbo machine as recited in claim 1, wherein the plurality of circumferentially spaced apart channels are adapted and configured to facilitate fluid communication between the first inlet area and the first collector, and between the second inlet area and the second collector.
  • 5. A centrifugal turbo machine as recited in claim 1, further comprising an inducer, having a helical blade extending radially outward, rotatably mounted about the central axis of the housing for drawing fluid axially from the fluid inlet port to the first inlet area of the impeller disk.
  • 6. A centrifugal turbo machine as recited in claim 5, further comprising a partition, formed by the housing within the interior chamber for isolating the first inlet area from the second inlet area, having a helical flange for isolating a top of the inducer in fluid communication with the first inlet area and for isolating a bottom of the inducer in fluid communication with the second inlet area.
  • 7. A centrifugal turbo machine as recited in claim 1, wherein the housing further includes a partition within the interior chamber for isolating the first inlet area from the second inlet area.
  • 8. A centrifugal turbo machine as recited in claim 7, wherein the partition defines a third inlet area, the outlet conducts fluid from the second collector to the third inlet area and the housing defines a third collector outward of the impeller for receiving the fluid passed through the impeller from the third inlet area and a second outlet formed by the housing for conducting fluid from the third collector.
  • 9. A centrifugal turbo machine as recited in claim 1, further comprising a first elevated pressure outlet for conducting the fluid from the first collector to allow the centrifugal pump to supply the fluid at the first elevated pressure and the second elevated pressure.
  • 10. A centrifugal turbo machine as recited in claim 1, wherein the first collector and the second collector are diametrically opposed from one another relative to the central axis of the housing.
  • 11. A centrifugal turbo machine as recited in claim 1, wherein the plurality of circumferentially spaced apart channels are bifurcated adjacent an outer diameter of the impeller.
  • 12. A centrifugal turbo machine as recited in claim 1, wherein the impeller is configured in such a manner so that at least 70% of the circumferentially spaced apart channels are in fluid communication with the first and second inlet areas.
  • 13. A centrifugal pump for an engine, comprising:a) a housing having a fluid inlet for receiving fluid at an initial pressure and an interior chamber defining a central axis; b) an impeller disposed within the interior chamber of the housing and mounted for rotation about the central axis, the impeller defining first and second sealingly isolated inlet areas and having opposed upper and lower disk surfaces, the upper surface having a plurality of circumferentially spaced apart channels formed therein for conducting fluid from the inlet areas in a radially outward direction upon rotation of the impeller disk so as to increase fluid pressure, wherein the plurality of circumferentially spaced apart channels are intermediate the upper and lower disk surfaces; c) a first collector formed by the housing for receiving the fluid from the first inlet area via the channels at a first elevated pressure relative to the initial pressure; d) a second collector formed by the housing for receiving fluid from the second inlet area via the channels at a second elevated pressure relative to the first elevated pressure, the second collector being sealingly isolated from the first collector; e) a cross-over conduit formed by the housing for conducting fluid from the first collector to the second inlet area of the impeller disk; and f) an outlet formed by the housing for conducting fluid from the second collector.
  • 14. A centrifugal pump as recited in claim 13, wherein the first and second collectors are sealingly isolated by sealing lands defined by the housing.
  • 15. A centrifugal pump as recited in claim 13, wherein the plurality of circumferentially spaced apart channels are adapted and configured to facilitate fluid communication between the first inlet area and the first collector, and between the second inlet area and the second collector.
  • 16. A centrifugal pump as recited in claim 13, further comprising an inducer rotatably mounted about the central axis of the housing for drawing fluid axially from the fluid inlet to the first inlet area of the impeller disk.
  • 17. A centrifugal pump as recited in claim 13, further comprising a partition within an inner diameter of the impeller formed by the housing for sealingly isolating the first inlet area from the second inlet area.
  • 18. A centrifugal pump as recited in claim 17, wherein the partition further includes a flange for directing the fluid to the first inlet area and for isolating the first inlet area from the second inlet area.
  • 19. A centrifugal pump for a gas turbine engine, comprising:a) a housing having a fluid inlet port for receiving fluid at an initial pressure and an interior chamber defining a central axis; b) an impeller disk disposed within the interior chamber of the housing and mounted for rotation about the central axis, the impeller disk defining first and second inlet areas and having a plurality of circumferentially spaced apart channels formed therein which extend from the inlet areas for conducting fluid in a radially outward direction upon rotation of the impeller disk so as to increase a fluid pressure; c) an inducer, disposed within the interior chamber of the housing and mounted for rotation about the central axis to draw fluid axially, the inducer having a top portion in fluid communication with the first inlet area and a bottom portion in fluid communication with the second inlet area; d) a first collector formed by the housing for receiving the fluid from the first inlet area via the channels at a first elevated pressure relative to the initial pressure; e) a second collector formed by the housing for receiving fluid from the second inlet area via the channels at a second elevated pressure relative to the first elevated pressure; f) a partition within the interior chamber of the housing for isolating the first inlet area from the second inlet area, the partition having a helical flange for isolating the top portion of the inducer from the bottom portion of the inducer; g) a cross-over conduit formed by the housing for conducting fluid from the first collector to the second inlet area of the impeller disk; and h) an outlet formed by the housing for conducting fluid from the second collector.
  • 20. A centrifugal pump as recited in claim 19, wherein the housing further defines sealing lands with the impeller disk for sealingly isolating the first and second collectors.
  • 21. A centrifugal pump as recited in claim 19, wherein the plurality of circumferentially spaced apart channels are adapted and configured to facilitate fluid communication fluid between the first inlet area and the first collector, and between the second inlet area and the second collector.
  • 22. A centrifugal pump as recited in claim 19, further comprising a second outlet in fluid communication with the first collector area for providing fluid at the first elevated pressure.
CROSS-REFERENCE TO RELATED APPLICATION

This application claims priority to U.S. Provisional Patent Application No. 60/151,998, filed Sep. 1, 1999, which is incorporated herein by reference in its entirety.

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