US3130679A - Nonclogging centrifugal pump - Google Patents

Nonclogging centrifugal pump Download PDF

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US3130679A
US3130679A US243112A US24311262A US3130679A US 3130679 A US3130679 A US 3130679A US 243112 A US243112 A US 243112A US 24311262 A US24311262 A US 24311262A US 3130679 A US3130679 A US 3130679A
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impeller
chamber
vanes
inlet
near
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US243112A
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Leonard H Sence
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Allis Chalmers Corp
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Allis Chalmers Corp
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    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04DNON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00Details, component parts, or accessories
    • F04D29/18Rotors
    • F04D29/22Rotors specially for centrifugal pumps
    • F04D29/2238Special flow patterns
    • F04D29/225Channel wheels, e.g. one blade or one flow channel
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04DNON-POSITIVE-DISPLACEMENT PUMPS
    • F04D7/00Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts
    • F04D7/02Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts of centrifugal type
    • F04D7/04Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts of centrifugal type the fluids being viscous or non-homogenous

Description

April 28, 1964 1 H. SENCE 3,130,679

NONCLOGGING CENTRIFUGAL PUMP Filed Dec. 7, 1962 2 Sheets-Sheet l April 1964 H. SENCE 3,130,679

NONCLOGGING CENTRIFUGAL PUMP I Filed Dec. 7, 1962 2 Sheets-Sheet 2 United States Patent O 3,130,679 NONCLOGGIING CENTRIFUGAL PUMP Leonard H. Sense, Milford, Ohio, assignor to Allis-Chalmers Manufacturing Company, Milwaukee, Wis.

Filed Dec. 7, 1962, Ser. No. 243,112 9 Claims. (Cl. 103-103) This invention relates generally to centrifugal pumps. More specifically this invention relates to non-clogging, solids handling centrifugal pumps.

There has long been a problem in the hydraulic industry in connection with pumping solid material or fibrous material. These materials tend to clog the impeller of a centrifugal pump. However, there is a trend toward pumping more and larger solid material suspended in liquids. Onp way of solving this problem is to take a conventional centrifugal pump impeller and position it in a recessed area alongside a swirl or pumping chamber. The impeller is spaced from the opposing wall of the pump casing a distance equal to the diameter of the inlet of the pump so that any material entering the pumping chamber can be pumped outward through the discharge without engaging the impeller vanes. Although pumps of this type have been successful to a certain degree, they can only develop a very limited head and their eflieiency is extremely low. As a result, such a pump is used only where it is absolutely necessary to pump solids of such a size that they frequently clog the impeller of a conventional centrifugal pump.

Applicant overcomes the problems mentioned above by providing a unique impeller which permits the use of the vanes in the pumping chamber and is still capable of pumping any solid which enters the inlet of the pump. The impeller vanes are formed so that they are very narrow near the center of the impeller and gradually widened to extend substantially across the impeller chamber near the periphery of the impeller. The vanes are arranged so that they combine with the backplate of the impeller and the casing to define a passageway extending from the eye of the impeller to its periphery which has a minimum size equal to a sphere of the same diameter as the inlet of the pump. Such a pump is truly nonclogging in that there is a continuous path through the pumping chamber which is the equivalent size of a sphere equal to the diameter of the inlet. Furthermore, since the vanes of the impeller are positioned in the pumping chamber, it utilizes the characteristics of a true centrifugal pump and hence can develop heads and eflicieneies comparable to a conventional centrifugal pump.

Therefore, it is the object of this invention to provide a new and improved centrifugal pump.

Another object of this invention is to provide a nonclogging solids handling pump with improved head and efliciency.

Other objects and advantages will be apparent from the following description when read in connection with the accompanying drawings in which:

FIG. 1 is a cross sectional view of a centrifugal pump embodying the impeller of this invention;

FIG. 2 is an end view taken along the line II--II of FIG. 1 of the impeller of this invention; and

FIG. 3 shows an alternate embodiment of this invention in which the impeller vanes are curved.

The pump assembly 9 illustrated in FIG. 1 comprises generally a pump casing 16 having an inlet 11 and a discharge 12. The casing defines an impeller or pumping chamber 13 in which an impeller 14 of this invention is positioned. The chamber 13 has a peripheral volute 15 to gather the discharge from the impeller and direct it into the discharge nozzle or opening 12.

The impeller 14 is connected to a shaft 17 which ex- 3,130,679 Patented Apr. 28, 1964 tends rearwardly from the pump casing 1% to a source of power. The shaft 17 is surrounded by a conventional shaft sleeve 16 and a suitable seal illustrated as a stufling box 18 having the usual packing 19 and a gland 28) held in place by suitable bolts. The shaft 17 is also surrounded by a bearing and bearing cartridge 23 which is in turn mounted in a bearing bracket 24. The bearing bracket is in turn connected to the pump casing 10 and a base member 25.

The pump 9 is also equipped with a rear cover plate 28 which in this particular embodiment surrounds the stuffing box 13 and is positioned adjacent the rear plate or shroud 2% of the impeller 14. The rear cover plate 28 is recessed into a cylindrical neck portion 39 of the pump casing 10 so as to be slightly spaced from the impeller chamber 13. The rear shroud 29 of the impeller is also partially recessed into the cylindrical neck 30 so that the front edge of the shroud 2? is aligned with the rear surface 31 of the impeller chamber 13. This is to avoid the formation of any sharp corners or surfaces which would tend to impede the progress of solids or fibers as they go through the impeller chamber.

The hub 39 of the impeller is provided with an axial bore 4! which is threaded for connection to the end of the shaft 17. As shown in FIGS. 1 and 2, the vanes 35 are areuately spaced around the shroud 29 and extend from near the center of the shroud plate 2? radially outward to its periphery. The thickness 42 of the vanes is substantially the same throughout their length although it could be varied if desired. However, the depth or width 43 of the vanes 35 varies from a very narrow width near the hub 39 of the impeller to a maximum width near the periphery of the impeller at which point the vanes extend almost entirely across the impeller chamber 13. However, in many applications it is preferred that the edge of the vane be spaced from the wall of the impeller chamber a suflicient distance to form a fluid passageway and thereby avoid any kind of a constriction about which stringy material such as found in paper pulp can get caught and clog the pump.

The vanes 35, the shroud plate 29 and the wall 36 of the impeller chamber 13 combine to define a plurality of fluid impelling passages 45 that extend from the inlet end of the pump to the discharge. The minimum size of these passageways 45 is equivalent to a sphere of the same diameter as the inlet 11 of the pump. Thence, any solid material entering the inlet of the pump can pass through one of these passages through the impeller chamber into the discharge. The minimum size of these passages is made possible by forming the leading edge 45 of the vanes so that it curves away from the Wall of the impeller chamber near the hub of the impeller where the arcuate space between adjacent vanes is very small. In this area the distance between the edge 46 of the vane and the wall 36 of the casing is substantially equal to the diameter of the inlet.

As the vane extends radially outward, the edge 46 of the vane curves toward the opposing wall surface 36 of the impeller chamber. In areas radially outward from the hub, the sphere can move between adjacent vanes 35 and a portion of the sphere extends inwardly from the edge of the vanes toward the shroud plate 29 of the impeller. In this position it does not require as much space between the edge 46 of the impeller vane and the casing wall 36 to pass a sphere the size of the inlet. For this reason the edge of the vane can extend closer to the opposing wall surface as the vane extends radially outward. The curve on the edge of the vanes continues until a point is reached where the distance between adjacent vanes is equal to the diameter of the inlet or the diameter of the theoretical sphere which is to be passed through the pump. At this point, the blades or vanes 35 could extend all the any solid which can enter the inlet of the s a es a 3 way to the opposing wall surface 36. However, as mentioned above, it is preferable to keep a sufllcient clearance between the wall surface and the tip of the vanes to avoid any restrictions to the flow through the pump of any solids or fibers suspended in the liquids.

In an alternate embodiment illustrated in FIG. 3, the entire impeller vanes 43 are curved backwardly as the vane extends outwardly to the periphery or rim of the impeller. This is in accord with conventional practices in the manufacture of centrifugal pumps and is done to further improve the hydraulic efiiciency of the pump. However, the same configuration of the leading edge of the vanes that is shown in FIG. 1 is carried out in this embodiment on the vanes 48. Hence, the width of the impeller vanes 48 near the hub is very small and gradually gets larger as the vane extends radially outward until it reaches its full width near the outer periphery of the impeller.

In the preferred embodiment we have illustrated a pump having a circular volute for collecting the fluid discharged from the impeller. However, it is obvious that this impeller could be used with a pump having a conventional or true volute type casing such as shown in FIG. 3 as well as the circular casing. The circular or uniform clearance type of casing has better nonclogging action.

In operation, as the impeller 14 begins to rotate, liquid with solids entrained therein are drawn in through the inlet 11. This liquid is then acted upon by the impeller and thrown radially outward. Any solids in the liquid move through the impelling passages defined between the vanes 35, the internal wall surface 36 of the impeller chamber and the rear shroud 29. In this way, pump can be impelled through the impeller into the discharge without clogging the pump.

The position of the impeller 14 relative to casing wall 36 can be varied by changing the position of the bearing cartridge 23 in housing 42 relative to the pump casing it). This can be done by rotating adjusting bolt or other means well known in the art. As is apparent from FIG. 1, there is sufi'icient space between the rear cover 28 of the pump and rear shroud 29 of impeller 14 to allow for some adjustment of the spacing between the impeller and its opposing wall surface.

Although but one embodiment has been illustrated and described, it will be apparent to those skilled in the art that various modifications and changes can be made therein without departing from the spirit of the invention or the scope of the appended claims.

Having now particularly described and ascertained the nature of my said invention and the manner in which it is to be performed, I declare that what I claim is:

1. A centrifugal pump comprising: a casing having walls defining an impeller chamber, said chamber having an axial inlet and a radially spaced discharge opening, an impeller mounted for rotation in said chamber, said impeller having a rear shroud plate and a plurality of arcuately spaced substantially radially extending vanes mounted thereon, said vanes extending inward to near the center of said impeller, the depth of said vanes being smaller near the center of said impeller than near its outer periphery, the radially outer portion of said vanes extendmg across substantially the entire width of said chamber, said vanes being arranged on said impeller so as to define with said shroud plate and the opposing said wall of said impeller chamber a plurality of passages continuous from the inlet of said chamber to said outlet, the minimum size of said passages being at least equal to a sphere of the same diameter as the width of said inlet, whereby any solid body entering said chamber through said inlet can be passed through said impeller to said discharge.

2. A centrifugal pump comprising: a casing having walls defining an impeller chamber, said chamber having an axial inlet and a radially spaced discharge opening,

i an impeller mounted for rotation in said chamber, said impeller having a rear shroud plate and a plurality of arcuately spaced vanes mounted thereon, said vanes extending from the periphery of said plate radially inward to near the center of said impeller, the width of said vanes being smaller near the center of said impeller than near its outer periphery, the radially outer portion of said vanes extending across substantially the entire width of said chamber, said vanes being arranged on said impeller so as to define with said shroud plate and the opposing said wall-of said impeller chamber a plurality of passages continuous from the inlet of said chamber to said outlet, the minimum size of said passages being at least equal to a sphere of the same diameter as the width of said inlet, whereby any solid body entering said chamber through said inlet can be passed through said impeller to said discharge.

3. A centrifugal pump comprising: a casing having walls defining an impeller chamber having an axial inlet, said chamber having a peripheral uniform clearance volute connected to a discharge nozzle, an impeller mounted for rotation in said chamber, said impeller having a rear shroud plate and a plurality of arcuately spaced substantially radially extending vanes mounted thereon, said vanes extending inward to near the center of said impeller, the depth of said vanes being smaller near the center of said impeller than near its outer periphery, the radially outer portion of said vanes extending across substantially the entire width of said chamber, said vanes being arranged on said impeller so as to define with said shroud plate and the opposing said wall of said impeller chamber a plurality of passages continuous from the inlet of said chamber to said outlet, the minimum size of said passages being at least equal to a sphere of the same diameter as the width of said inlet, whereby any solid particle entering said chamber can be passed through said impeller to said discharge.

4. A centrifugal pump comprising: a casing having walls defining an impeller chamber having an axial inlet, said chamber having peripheral gradually increasing clearance volute terminating in a discharge nozzle, an impeller mounted for rotation in said chamber, said impeller having a rear shroud plate and a plurality of arcuately spaced substantially radially extending vanes mounted thereon, said vanes extending inward to near the center of said impeller, the depth of said vanes being smaller near the center of said impeller than near its outer periphery, the radially outer portion of said vanes extending across substantially the entire width of said chamber, said vanes being arranged on said impeller so as to define with said shroud plate and the opposing said wall of said impeller chamber a plurality of passages continuous from the inlet of said chamber to said outlet, the minimum size of said passages being at least equal to a sphere of the same diameter as the width of said inlet, whereby any solid particle entering said chamber can be passed through said impeller to said discharge.

5. A centrifugal pump comprising: a casing having walls defining an impeller chamber, said chamber having an axial inlet and a radially spaced discharge opening, an impeller mounted for rotation in said chamber, said impeller having a rear shroud plate and a plurality of arcuately spaced substantially radially extending vanes mounted thereon, said vanes extending inward to near the center of said impeller, the depth of said vanes being smaller near the center of said impeller than near its outer periphery, the radially outer portion of said vanes extending partially across said chamber, said vanes being arranged on said impeller so as to define with said shroud plate and said opposing wall of said chamber a plurality of separate passages continuous from the inlet of said chamber to said outlet, the minimum size of said passages being at least equal to a sphere of the same diameter as the width of said inlet, whereby any solid particle entermg said chamber can be passed through said impeller to said discharge.

6. A centrifugal pump comprising: a casing having walls defining an impeller chamber, said chamber having an axial inlet and a radially spaced discharge opening, an impeller mounted for rotation in said chamber, said impeller having a rear shroud plate and a plurality of arcuately spaced vanes mounted thereon, said vanes extending inward along a curved line from the periphery of said plate to near the center of said impeller, the width of said vanes being smaller near the center of said impeller than near its outer periphery, the radially outer portion of said vanes extending across substantially the entire width of said chamber and being arranged on said impeller so as to define with said shroud plate and said walls a plurality of independent passages continuous from the inlet of said chamber to said outlet, the minimum size of said passages being at least equal to a sphere of the same diameter as the width of said inlet, whereby any solid body entering said chamber through said inlet can be passed through said impeller to said discharge.

7. The centrifugal pump of claim 1 in which the tips of the vanes combined with the hub of the impeller to define a continuous smooth surface.

8. The centrifugal pump of claim 1 in which the walls defining the impeller chamber are substantially parallel.

9. The centrifugal pump of claim 1 in which the maximum depth of the vanes is at the outer periphery of the impeller.

References Cited in the file of this patent UNITED STATES PATENTS 2,635,548 Brawley Apr. 21, 1953 2,655,868 Lindau et al Oct. 20, 1953 2,785,930 Burnside Mar. 19, 1957 2,853,019 Thornton Sept. 23, 1958 2,958,293 Pray Nov. 1, 1960 FOREIGN PATENTS 542,597 France May 19, 1922 413,573 Great Britain of 1934 574,079 Great Britain Dec. 19, 1945 82,497 Switzerland Oct. 1, 1919

Claims (1)

1. A CENTRIFUGAL PUMP COMPRISING: A CASING HAVING WALLS DEFINING AN IMPELLER CHAMBER, SAID CHAMBER HAVING AN AXIAL INLET AND A RADIALLY SPACED DISCHARGE OPENING, AN IMPELLER MOUNTED FOR ROTATION IN SAID CHAMBER, SAID IMPELLER HAVING A REAR SHROUD PLATE AND A PLURALITY OF ARCUATELY SPACED SUBSTANTIALLY RADIALLY EXTENDING VANES MOUNTED THEREON, SAID VANES EXTENDING INWARD TO NEAR THE CENTER OF SAID IMPELLER, THE DEPTH OF SAID VANES BEING SMALLER NEAR THE CENTER OF SAID IMPELLER THAN NEAR ITS OUTER PERIPHERY, THE RADIALLY OUTER PORTION OF SAID VANES EXTENDING ACROSS SUBSTANTIALLY THE ENTIRE WIDTH OF SAID CHAMBER, SAID VANES BEING ARRANGED ON SAID IMPELLER SO AS TO DEFINE WITH SAID SHROUD PLATE AND THE OPPOSING SAID WALL OF SAID IMPELLER CHAMBER A PLURALITY OF PASSAGES CONTINUOUS FROM THE INLET OF SAID CHAMBER TO SAID OUTLET, THE MINIMUM SIZE OF SAID PASSAGES BEING AT LEAST EQUAL TO A SPHERE OF THE SAME DIAMETER AS THE WIDTH OF SAID INLET, WHEREBY ANY SOLID BODY ENTERING SAID CHAMBER THROUGH SAID INLET CAN BE PASSED THROUGH SAID IMPELLER TO SAID DISCHARGE.
US243112A 1962-12-07 1962-12-07 Nonclogging centrifugal pump Expired - Lifetime US3130679A (en)

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US243112A US3130679A (en) 1962-12-07 1962-12-07 Nonclogging centrifugal pump
GB4686263A GB1021468A (en) 1962-12-07 1963-11-27 Improvements in or relating to centrifugal pumps
CH1497063A CH397430A (en) 1962-12-07 1963-12-06 Centrifugal pump
DE19631453715 DE1453715A1 (en) 1962-12-07 1963-12-06 centrifugal pump

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Cited By (44)

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Publication number Priority date Publication date Assignee Title
US3238880A (en) * 1963-11-14 1966-03-08 Speedwell Res Ltd Pumps
US3247801A (en) * 1965-02-03 1966-04-26 Hydr O Matic Pump Co Self-priming sewage and trash pump
US3269325A (en) * 1963-07-29 1966-08-30 Mckee & Co Arthur G Pump
US3295456A (en) * 1965-04-12 1967-01-03 Cornell Mfg Co Pump
US3362628A (en) * 1964-02-12 1968-01-09 Sulzer Ag Turbine-type machine
US3367627A (en) * 1964-02-14 1968-02-06 Sulzer Ag Turbine-type machine construction
US3598502A (en) * 1968-03-14 1971-08-10 Harold Philip Sidney Paish Centrifugal pumps
US3759628A (en) * 1972-06-14 1973-09-18 Fmc Corp Vortex pumps
US3837627A (en) * 1972-06-07 1974-09-24 Allis Chalmers Method and apparatus for gasifying a liquid
US3918637A (en) * 1971-11-23 1975-11-11 Eberspaecher J Heater assembly for motor vehicle with water-cooled combustion engine
US4193737A (en) * 1977-09-22 1980-03-18 Lemmon George H Fish pump
US4521151A (en) * 1980-03-07 1985-06-04 Joy Manufacturing Holdings Limited Centrifugal slurry pump
US4915583A (en) * 1986-03-17 1990-04-10 Aciers Et Outillage Peugeot Radial-flow fan in particular for the air-conditioning of a motor vehicle
US4998861A (en) * 1988-12-16 1991-03-12 Hitachi, Ltd. Drainage pump
US5137424A (en) * 1990-05-10 1992-08-11 Daniel William H Pump unit
EP0760427A1 (en) * 1995-08-31 1997-03-05 Giw Industries Inc. High capacity, large sphere passing, slurry pump
US20060165523A1 (en) * 2005-01-21 2006-07-27 Rozario Frederick J Centrifugal water pump
US20080213111A1 (en) * 2002-07-12 2008-09-04 Cooper Paul V System for releasing gas into molten metal
US20080304970A1 (en) * 2003-07-14 2008-12-11 Cooper Paul V Pump with rotating inlet
US20080314548A1 (en) * 2007-06-21 2008-12-25 Cooper Paul V Transferring molten metal from one structure to another
US20090269191A1 (en) * 2002-07-12 2009-10-29 Cooper Paul V Gas transfer foot
US7906068B2 (en) 2003-07-14 2011-03-15 Cooper Paul V Support post system for molten metal pump
US20120189452A1 (en) * 2010-07-20 2012-07-26 Itt Manufacturing Enterprises, Inc. Impeller Attachment Method
US8366993B2 (en) 2007-06-21 2013-02-05 Cooper Paul V System and method for degassing molten metal
US8444911B2 (en) 2009-08-07 2013-05-21 Paul V. Cooper Shaft and post tensioning device
US8449814B2 (en) 2009-08-07 2013-05-28 Paul V. Cooper Systems and methods for melting scrap metal
US8524146B2 (en) 2009-08-07 2013-09-03 Paul V. Cooper Rotary degassers and components therefor
US8529828B2 (en) 2002-07-12 2013-09-10 Paul V. Cooper Molten metal pump components
US8535603B2 (en) 2009-08-07 2013-09-17 Paul V. Cooper Rotary degasser and rotor therefor
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CH82497A (en) * 1919-03-19 1919-10-01 Josef Bucher Centrifugal pump for solid constituents leading liquid
FR542597A (en) * 1921-02-16 1922-08-17 Mach Albert Stalder S A Fab De Centrifugal pump
GB413573A (en) * 1933-12-20 1934-07-19 Harry Winch Sealing means for the shafts of rotary pumps and the like
GB574079A (en) * 1944-02-18 1945-12-19 F W Brackett & Company Ltd A new or improved centrifugal pump
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US2785930A (en) * 1953-08-24 1957-03-19 Le Roy B Lorenz Apparatus for pumping solids
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Cited By (92)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3269325A (en) * 1963-07-29 1966-08-30 Mckee & Co Arthur G Pump
US3238880A (en) * 1963-11-14 1966-03-08 Speedwell Res Ltd Pumps
US3362628A (en) * 1964-02-12 1968-01-09 Sulzer Ag Turbine-type machine
US3367627A (en) * 1964-02-14 1968-02-06 Sulzer Ag Turbine-type machine construction
US3247801A (en) * 1965-02-03 1966-04-26 Hydr O Matic Pump Co Self-priming sewage and trash pump
US3295456A (en) * 1965-04-12 1967-01-03 Cornell Mfg Co Pump
US3598502A (en) * 1968-03-14 1971-08-10 Harold Philip Sidney Paish Centrifugal pumps
US3918637A (en) * 1971-11-23 1975-11-11 Eberspaecher J Heater assembly for motor vehicle with water-cooled combustion engine
US3837627A (en) * 1972-06-07 1974-09-24 Allis Chalmers Method and apparatus for gasifying a liquid
US3759628A (en) * 1972-06-14 1973-09-18 Fmc Corp Vortex pumps
US4193737A (en) * 1977-09-22 1980-03-18 Lemmon George H Fish pump
US4521151A (en) * 1980-03-07 1985-06-04 Joy Manufacturing Holdings Limited Centrifugal slurry pump
US4915583A (en) * 1986-03-17 1990-04-10 Aciers Et Outillage Peugeot Radial-flow fan in particular for the air-conditioning of a motor vehicle
US4998861A (en) * 1988-12-16 1991-03-12 Hitachi, Ltd. Drainage pump
US5137424A (en) * 1990-05-10 1992-08-11 Daniel William H Pump unit
EP0760427A1 (en) * 1995-08-31 1997-03-05 Giw Industries Inc. High capacity, large sphere passing, slurry pump
US5813833A (en) * 1995-08-31 1998-09-29 Giw Industries, Inc. High capacity, large sphere passing, slurry pump
US8409495B2 (en) 2002-07-12 2013-04-02 Paul V. Cooper Rotor with inlet perimeters
US9435343B2 (en) 2002-07-12 2016-09-06 Molten Meal Equipment Innovations, LLC Gas-transfer foot
US20080213111A1 (en) * 2002-07-12 2008-09-04 Cooper Paul V System for releasing gas into molten metal
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