US20100061841A1 - Froth handling pump - Google Patents
Froth handling pump Download PDFInfo
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- US20100061841A1 US20100061841A1 US12/543,303 US54330309A US2010061841A1 US 20100061841 A1 US20100061841 A1 US 20100061841A1 US 54330309 A US54330309 A US 54330309A US 2010061841 A1 US2010061841 A1 US 2010061841A1
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- pump
- vanes
- impeller
- outlet
- shroud
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/18—Rotors
- F04D29/22—Rotors specially for centrifugal pumps
- F04D29/2261—Rotors specially for centrifugal pumps with special measures
- F04D29/2277—Rotors specially for centrifugal pumps with special measures for increasing NPSH or dealing with liquids near boiling-point
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/18—Rotors
- F04D29/22—Rotors specially for centrifugal pumps
- F04D29/2261—Rotors specially for centrifugal pumps with special measures
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D9/00—Priming; Preventing vapour lock
- F04D9/001—Preventing vapour lock
- F04D9/002—Preventing vapour lock by means in the very pump
- F04D9/003—Preventing vapour lock by means in the very pump separating and removing the vapour
Definitions
- the present invention relates to the field of centrifugal slurry pumps, and particularly, to froth pumps for mining applications where flotation methods are utilized.
- Centrifugal pumps employ centrifugal force to lift liquids from a lower to a higher level or to produce a pressure.
- This type of pump in its is simplest form, comprises an impeller consisting of a connecting hub with a number of vanes and shrouds, rotating in a volute collector or casing. Liquid drawn into the center, or eye, of the impeller is picked up by the vanes and accelerated to a high velocity by rotation of the impeller. It is then discharged by centrifugal force into the casing and out the discharge branch of the casing. When liquid is forced away from the center of the impeller, a vacuum is created and more liquid flows into the center of the impeller. Consequently, there is a flow through the pump.
- centrifugal pumps including the type used to pass solid and liquid mixtures. These are known as slurry pumps.
- Froth handling pumps are a special application of centrifugal slurry pumps.
- the need to pump froth occurs in many mining applications where flotation methods are utilized. These pumps take advantage of the surface tension effects between pulverized ore and fine bubbles to separate the ore from the waste rock by floating one away from the other.
- the various mining applications include mining for metallic ores such as copper, iron, etc., and in the oil sand industry, where the components of froth include bitumen, water, and air.
- a mixture of approximately 10% bitumen and 90% sand is mined directly from the ground and the bitumen is separated from the sand for conversion to synthetic crude oil. As the separation takes place, gas develops, creating a bitumen froth with approximately a 15 percent to 30 percent gas/air content.
- froth handling pumps often “air lock.” This occurs when gases accumulate in the suction of the pump under the action of the centrifugal forces operating on the fluid in the passages of a rotating impeller to form an air/gas bubble, which partially blocks the suction and significantly degrades pump performance (as much as 40 percent to 70 percent loss in both flow and head). With viscous flows like bitumen, for example, this air lock can be particularly difficult to remedy due to the laminar, or near laminar, nature of the high viscosity flow.
- froth pumps cannot typically produce as much head as non-froth applications, being limited by the presence of air (which cannot be effectively energized by the centrifugal pump), by the blockage which occurs as the air lock begins to form, and by the maximum speed at which the pump can be run before net positive suction head available (NPSHA) to the pump suction falls below the minimum required to prevent cavitation in the pump impeller.
- the head may be limited to as little as 30 meters to 40 meters in viscous froth applications, due to the additional viscous friction losses. This often necessitates that a number of pumps be placed in service to provide the necessary capacity for the mining and pumping process.
- the present invention is directed to a froth handling pump, which significantly minimizes or eliminates the problems described herein during ore or bitumen froth pumping.
- ore refers to any of the many minerals and metals, which may be extracted through mining.
- bitumen refers to any of various flammable mixtures of hydrocarbons and other substances, occurring naturally or obtained by distillation from coal or petroleum.
- one aspect of the present invention is directed to a froth handling pump, which comprises either a conventional, or modified, pump casing having an inlet side and a rear (hub) side.
- a novel impeller has been invented, which can produce a head equal to or greater than existing froth slurry pumps, but without the application of some of the conventional methods for reducing the NPSH required, such as an enlarged suction diameter, an inducer or auxiliary impeller, etc., or by increasing the NPSHA beyond what is normally present. This, in effect, keeps the size of the froth handling pump smaller and more economical.
- the pump achieves heads of 50 meters or higher at viscosities up to 3,000 cP and with NPSHA less than 10 meters by application of a very high vane outlet angle. While typical centrifugal pump outlet angles range from between about 15 degrees and 40 degrees, with 20 degrees to 25 degrees considered optimal, the impeller of the present invention has a vane outlet angle of between about 80 degrees and 100 degrees, with 90 degrees being optimal. Unexpectedly, the resulting efficiency is at least about 73 percent peak efficiency (with clear water).
- the rear shroud of the impeller includes an inner face and an outer face, with a plurality of vent holes formed through the shroud for the passage of gases to an attached de-aeration chamber.
- a plurality of generally radially oriented clearing vanes are formed on the outer face of the rear shroud. The clearing vanes are configured to create a pressure at the back side of the vent holes that is less than the fluid side so that vented gases are drawn into the de-aeration chamber.
- An outlet vent is provided proximate the top of the de-aeration chamber for venting the gases to the atmosphere or to a connected vent line.
- front shrouds are generally used in froth pump impellers, including one embodiment described herein, it has been found that removal of the front shroud of the impeller further serves to reduce the occurrence of air locks and to maintain maximum pump head and flow.
- FIG. 1 is a perspective view of an embodiment of the froth handling pump of the present invention.
- FIG. 2 is a side elevational cross-sectional view of the froth handling pump of FIG. 1 .
- FIG. 3 is a perspective view of one embodiment of the impeller of the froth handling pump of FIG. 1 .
- FIG. 4 is a front view of the impeller of FIG. 3 with the front shroud removed to show the vanes.
- FIG. 5 is a schematic illustration of the gaseous venting scheme of the froth handling pump of FIG. 1 .
- FIG. 6 is a side rear view of the shroud of the impeller of FIG. 3 , illustrating the arrangement and geometry of the clearing vanes.
- FIG. 7 is a rear perspective view illustrating the optional auxiliary impeller on the rear shroud of the impeller of FIG. 3 .
- FIG. 8 is a perspective view of the de-aeration chamber of the froth handling pump of FIG. 1 .
- FIG. 9 is a side rear view of the de-aeration chamber of FIG. 8 .
- FIG. 10 is a perspective view of an alternative embodiment of the impeller of the froth handling pump of FIG. 1 .
- FIG. 11 is a front view of the impeller of FIG. 10 .
- FIG. 12 graphically demonstrates the head loss performance of the froth handling pump of the present invention with the closed-shroud configuration pumping a water-soap froth.
- FIG. 13 graphically demonstrates the flow loss performance of the froth handling pump of the present invention with the open-shroud configuration pumping a water-soap froth.
- the froth handling pump of the present invention is shown generally as 100 .
- the froth handling pump 100 comprises a centrifugal pump casing 120 , a novel impeller 140 mounted in the casing, and a de-aeration chamber 160 mounted to the rear side 124 of the pump casing 120 .
- a conventional pump shaft 170 passes through the de-aeration chamber 160 and attaches to the hub 141 of the impeller 140 .
- the shaft 170 is then mounted on a conventional pedestal 190 via a conventional bearing and bearing housing arrangement (not shown).
- the pump casing 120 of the froth handling pump of the present invention is a conventional design for centrifugal slurry pumps; however, a modified, or more open inlet side may be contemplated for a particular froth handling application, or for alternative impeller configurations, as described below. Alternatively, as described in detail below, the front shroud may be eliminated in its entirety.
- the novel impeller 140 of the froth handling pump 100 is illustrated in detail.
- one embodiment of the impeller 140 comprises a front shroud 142 , a rear shroud 144 , and a plurality of pumping vanes 146 .
- the front shroud 142 is conventional for a centrifugal slurry pump; however, in an alternative embodiment, the front shroud 142 also may be modified for a particular froth handling application and could include a more open configuration, having a larger suction inlet diameter.
- the impeller 140 of this illustrated embodiment comprises a novel pumping vane 146 arrangement.
- full size vanes 146 a and splitter vanes 146 b are arranged in an alternating fashion about the circumference of the impeller 140 .
- Splitter vanes 146 b are shorter, thus not extending radially inwardly as far toward the suction eye 147 as the fuller size pumping vanes 146 a .
- the number of pumping vanes 146 a , 146 b is maximized within the constraints of vane thickness and minimum required passage size. It has been found, however, that the use of splitter vanes 146 b helps to increase the effective number of pumping vanes 146 without “choking” the suction eye 147 of the impeller.
- passage size refers to the minimum mid-channel clearance between two adjacent pumping vanes 146 .
- the pumping vane 146 geometry extends between the front 142 shroud (when included) and rear 144 shroud of the impeller 140 in a manner that provides maximum efficiency.
- the inventors have found that the size of the impeller 140 , and thus the overall size of the pump 100 , can be minimized by employing pumping vanes 146 that have a combination of high angle outlets, for maximum head, and conventional lower angle inlets for developing sufficient NPSH performance.
- an outlet vane angle may be between about 80 degrees and 100 degrees, with 90 degrees being optimal.
- pumping vane 146 angles are defined relative to the tangent of the impeller circumference; e.g., an outlet angle of 0 degrees would be tangential to the circumference of the impeller, while an outlet angle of 90 degrees is radial with respect to the center of the impeller, or perpendicular to the tangent of the impeller.
- While the exemplary embodiments shown herein comprise an arrangement of 12 alternating full size 146 a and splitter 146 b pumping vanes, other pumping vane configurations also may provide suitable head and pumping efficiencies.
- the pumping vane 146 configuration as shown, having outlet angles of about 90 degrees, the inventors have found unexpectedly that a relative efficiency of at least about 73 percent may be achieved when pumping clear water.
- vent holes 148 are formed through the rear shroud 144 of the impeller 140 .
- the vent holes 148 are located for the effective venting of gases therethrough.
- the vent holes 148 must provide a minimum opening of about 2 inches in diameter, or, if not circular, an area of about 3.14 square inches.
- FIG. 5 the principle of operation of the novel froth handling pump 100 is schematically illustrated.
- the gas shown as G in FIG. 5
- the continuous accumulation of gas during operation of the pump will eventually create “choking” of the impeller passage, resulting in cavitation and air lock of the impeller.
- vent holes 148 By providing vent holes 148 , as shown in FIG. 6 , at the appropriate circumferential locations through the rear shroud 144 of the impeller 140 , the gases have outlets to escape from the impeller main passages.
- the size, shape, and relative positions of these vent holes 148 are influenced by the quantity and anticipated location for gas accumulation. In the illustrated embodiments shown in the Figures, the positions of the vent holes 148 correspond approximately to the suction diameter of the impeller.
- the present invention comprises an impeller 140 having a plurality of clearing vanes 149 a , 149 b formed on the outer face 144 a of the rear shroud 144 .
- These clearing vanes serve several purposes: (1) they assist in balancing the axial thrust of the rotating impeller, and (2) they exert a static pressure equal to or greater than the main impeller vanes to restrict the inwardly entry of main (liquid) flow from the impeller outlet.
- the clearing vanes 149 a and 149 b are formed such that, as the impeller rotates, the clearing vanes 149 a , 149 b create a pressure at the outer face 144 a that is lower than the pressure in the impeller suction eye 147 . By creating this differential pressure, the gases are drawn through the impeller vent holes 148 into the attached de-aeration chamber 160 . As shown in FIG. 6 , the clearing vanes 149 a , 149 b are radially-oriented (90 degrees) and extend substantially perpendicularly outward from the outer face 144 a of the rear shroud 144 .
- clearing vanes 149 a , 149 b there are 18 clearing vanes 149 a , 149 b , comprising 12 short vanes 149 a and 6 long vanes 149 b ; however, the total number of clearing vanes is not critical to the operation of the froth handling pump 100 of the present invention. Rather, the number, geometry, and angles of the clearing vanes are dependent upon the particular froth handling application.
- the number of clearing vanes 149 a , 149 b may be maximized.
- the clearing vanes 149 a , 149 b may need to be larger in diameter than the pumping vanes 146 by as much as 10 percent to obtain the desired pressure differential between the impeller suction eye 147 and the de-aeration chamber 160 .
- an auxiliary impeller configuration 180 may be rigidly mounted on the outer face 144 a of the rear shroud 144 .
- the inventors have found that this configuration assists in creating a negative pressure relative to the pumping vanes 146 .
- the outer radius of the auxiliary impeller configuration 180 is greater than the maximum radial position of the vent holes 148 to prevent gases from being trapped on the outer face 144 a.
- the de-aeration chamber 160 has an inlet opening 162 having a diameter that is dimensioned to extend outwardly beyond the maximum radial position of the vent holes 148 in the rear shroud 144 .
- the de-aeration chamber is thus rigidly coupled to the rear side 124 of the pump casing 120 by bolting or other conventional fastening means.
- pump casing 120 is modified from a conventional centrifugal pump casing, with an opening formed in the rear side 124 of the pump casing 120 corresponding in size to the inlet opening 162 of the de-aeration chamber 160 .
- the de-aeration chamber 160 comprises a housing 163 having an inner volume.
- the de-aeration chamber 160 is a passive component of the froth handling pump 100 construction; i.e., the chamber 160 has no moving or movable parts.
- an opening 165 is formed on the rear face 164 of the de-aeration chamber 160 for passage of the to pump shaft 170 therethrough the chamber 160 for mounting to the impeller hub 142 .
- At least one outlet 166 is formed for discharging the gases from the chamber 160 .
- the de-aeration chamber 160 may comprise a second outlet 168 .
- outlets 166 , 168 should be at least about 3 inches in diameter to prevent clogging and to adequately vent the anticipated volume of gases.
- the outlet 166 should be located at about 22.5 degrees or less of vertical (in either direction from the vertical) for sufficiently releasing the gases.
- the outlet 166 may be provided with a flange 167 so that it may be interconnected to a discharge line (not shown) leading to a location suitable for discharging the vented gases.
- the vented flow may include some liquid discharge that should be diverted to a sump or other drainage location.
- outlet 168 may be utilized for cleaning and drainage, as necessary.
- the impeller is an open-shroud configuration, comprising only a rear shroud 244 and a plurality of pumping vanes 246 , including full size vanes 146 a and splitter vanes 146 b .
- the pumping vanes 246 may be geometrically extrapolated outwardly axially toward the suction liner to compensate for the thickness of a front shroud.
- an outlet vane angle may be between about 80 degrees and 100 degrees, with 90 degrees being optimal.
- the configuration of the pump 100 including the de-aeration chamber 160 , are similar to the closed-shroud configuration of the pump 100 .
- the open-shroud configuration creates greater shear and turbulence between the pumping vanes and the suction liner of the pump, which breaks up air bubbles and further delays the formation of an air lock bubble.
- the inventors have found that this effectively increases the suction diameter, which reduces the velocity at the inlet edge of the impeller, and thereby increases the static pressure at the inlet edge.
- the diameter of the suction inlet of the pump casing 120 may be increased for the open-shroud impeller to provide more open suction, which is less subject to air blockage. This effectively reduces the velocity at the inlet edge of the impeller, and thereby increases the static pressure there, which delays vapor formation (cavitation).
- FIGS. 12 and 13 testing and performance data for both embodiments of the pump 100 are graphically illustrated. The testing was performed under similar conditions for both embodiments.
- a water-soap froth was formulated for the testing of the novel impellers.
- FIGS. 12 and 13 demonstrate the is performance of the open-shroud froth handling impeller compared to the closed-shroud embodiment described herein. Data is provided with the venting system open and closed, and at two different flowrates above and below the pump design flowrate.
- the open-shroud froth impeller resists air lock at a higher percentage of air than the closed-shroud froth impeller.
- the open-shroud froth impeller also exhibits a lower degree of losses than the closed-shroud design after air lock, with the venting system operational.
Abstract
A froth handling pump includes a pump casing, an impeller mounted within the casing, and a de-aeration chamber mounted to the rear side of the pump casing. The impeller comprises multiple pumping vanes, each of the vanes having an inlet angle and an outlet angle, wherein the outlet angle is greater than the inlet angle, the outlet angles terminating at a rear shroud. The rear shroud includes multiple vent holes for the passage of gases therethrough. The de-aeration chamber, which comprises an inner volume, includes an inlet formed on the inner side for receiving gases passing through the plurality of vent holes. At least one vent outlet is provided for the discharge of gases from the de-aeration chamber.
Description
- This is a continuation-in-part of application Ser. No. 12/208,747, filed Sep. 11, 2008, the content of which is incorporated herein in its entirety.
- The present invention relates to the field of centrifugal slurry pumps, and particularly, to froth pumps for mining applications where flotation methods are utilized.
- Centrifugal pumps, as the name implies, employ centrifugal force to lift liquids from a lower to a higher level or to produce a pressure. This type of pump, in its is simplest form, comprises an impeller consisting of a connecting hub with a number of vanes and shrouds, rotating in a volute collector or casing. Liquid drawn into the center, or eye, of the impeller is picked up by the vanes and accelerated to a high velocity by rotation of the impeller. It is then discharged by centrifugal force into the casing and out the discharge branch of the casing. When liquid is forced away from the center of the impeller, a vacuum is created and more liquid flows into the center of the impeller. Consequently, there is a flow through the pump. There are many forms of centrifugal pumps, including the type used to pass solid and liquid mixtures. These are known as slurry pumps.
- Froth handling pumps are a special application of centrifugal slurry pumps. The need to pump froth occurs in many mining applications where flotation methods are utilized. These pumps take advantage of the surface tension effects between pulverized ore and fine bubbles to separate the ore from the waste rock by floating one away from the other. The various mining applications include mining for metallic ores such as copper, iron, etc., and in the oil sand industry, where the components of froth include bitumen, water, and air. In the process of mining oil sands, for example, a mixture of approximately 10% bitumen and 90% sand is mined directly from the ground and the bitumen is separated from the sand for conversion to synthetic crude oil. As the separation takes place, gas develops, creating a bitumen froth with approximately a 15 percent to 30 percent gas/air content.
- While froth is widely pumped in mining applications and much is known about the process, a number of problems exist with froth pumps themselves and the pumping process. First, froth handling pumps often “air lock.” This occurs when gases accumulate in the suction of the pump under the action of the centrifugal forces operating on the fluid in the passages of a rotating impeller to form an air/gas bubble, which partially blocks the suction and significantly degrades pump performance (as much as 40 percent to 70 percent loss in both flow and head). With viscous flows like bitumen, for example, this air lock can be particularly difficult to remedy due to the laminar, or near laminar, nature of the high viscosity flow. Even if the pump is stopped, the bubble can remain within the pump casing or connecting piping and may be drawn back into the pump suction upon restart. Second, froth pumps cannot typically produce as much head as non-froth applications, being limited by the presence of air (which cannot be effectively energized by the centrifugal pump), by the blockage which occurs as the air lock begins to form, and by the maximum speed at which the pump can be run before net positive suction head available (NPSHA) to the pump suction falls below the minimum required to prevent cavitation in the pump impeller. The head may be limited to as little as 30 meters to 40 meters in viscous froth applications, due to the additional viscous friction losses. This often necessitates that a number of pumps be placed in service to provide the necessary capacity for the mining and pumping process.
- The present invention is directed to a froth handling pump, which significantly minimizes or eliminates the problems described herein during ore or bitumen froth pumping. As used herein, “ore” refers to any of the many minerals and metals, which may be extracted through mining. Also, as used herein, “bitumen” refers to any of various flammable mixtures of hydrocarbons and other substances, occurring naturally or obtained by distillation from coal or petroleum.
- Broadly, one aspect of the present invention is directed to a froth handling pump, which comprises either a conventional, or modified, pump casing having an inlet side and a rear (hub) side. A novel impeller has been invented, which can produce a head equal to or greater than existing froth slurry pumps, but without the application of some of the conventional methods for reducing the NPSH required, such as an enlarged suction diameter, an inducer or auxiliary impeller, etc., or by increasing the NPSHA beyond what is normally present. This, in effect, keeps the size of the froth handling pump smaller and more economical.
- The pump achieves heads of 50 meters or higher at viscosities up to 3,000 cP and with NPSHA less than 10 meters by application of a very high vane outlet angle. While typical centrifugal pump outlet angles range from between about 15 degrees and 40 degrees, with 20 degrees to 25 degrees considered optimal, the impeller of the present invention has a vane outlet angle of between about 80 degrees and 100 degrees, with 90 degrees being optimal. Unexpectedly, the resulting efficiency is at least about 73 percent peak efficiency (with clear water).
- The rear shroud of the impeller includes an inner face and an outer face, with a plurality of vent holes formed through the shroud for the passage of gases to an attached de-aeration chamber. A plurality of generally radially oriented clearing vanes are formed on the outer face of the rear shroud. The clearing vanes are configured to create a pressure at the back side of the vent holes that is less than the fluid side so that vented gases are drawn into the de-aeration chamber. An outlet vent is provided proximate the top of the de-aeration chamber for venting the gases to the atmosphere or to a connected vent line.
- Further, while front shrouds are generally used in froth pump impellers, including one embodiment described herein, it has been found that removal of the front shroud of the impeller further serves to reduce the occurrence of air locks and to maintain maximum pump head and flow.
- These and other aspects of the present invention will become apparent to those skilled in the art after a reading of the following description of exemplary embodiments when considered in conjunction with the drawings. It should be understood that both the foregoing general description and the following detailed description are exemplary and explanatory only and are not restrictive of the invention as claimed.
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FIG. 1 is a perspective view of an embodiment of the froth handling pump of the present invention. -
FIG. 2 is a side elevational cross-sectional view of the froth handling pump ofFIG. 1 . -
FIG. 3 is a perspective view of one embodiment of the impeller of the froth handling pump ofFIG. 1 . -
FIG. 4 is a front view of the impeller ofFIG. 3 with the front shroud removed to show the vanes. -
FIG. 5 is a schematic illustration of the gaseous venting scheme of the froth handling pump ofFIG. 1 . -
FIG. 6 is a side rear view of the shroud of the impeller ofFIG. 3 , illustrating the arrangement and geometry of the clearing vanes. -
FIG. 7 is a rear perspective view illustrating the optional auxiliary impeller on the rear shroud of the impeller ofFIG. 3 . -
FIG. 8 is a perspective view of the de-aeration chamber of the froth handling pump ofFIG. 1 . -
FIG. 9 is a side rear view of the de-aeration chamber ofFIG. 8 . -
FIG. 10 is a perspective view of an alternative embodiment of the impeller of the froth handling pump ofFIG. 1 . -
FIG. 11 is a front view of the impeller ofFIG. 10 . -
FIG. 12 graphically demonstrates the head loss performance of the froth handling pump of the present invention with the closed-shroud configuration pumping a water-soap froth. -
FIG. 13 graphically demonstrates the flow loss performance of the froth handling pump of the present invention with the open-shroud configuration pumping a water-soap froth. - Referring to the Figures in general, and to
FIGS. 1 and 2 in particular, the froth handling pump of the present invention is shown generally as 100. In its simplest embodiment, thefroth handling pump 100 comprises acentrifugal pump casing 120, anovel impeller 140 mounted in the casing, and ade-aeration chamber 160 mounted to therear side 124 of thepump casing 120. Aconventional pump shaft 170 passes through thede-aeration chamber 160 and attaches to the hub 141 of theimpeller 140. Theshaft 170 is then mounted on aconventional pedestal 190 via a conventional bearing and bearing housing arrangement (not shown). - As shown in
FIG. 2 , thepump casing 120 of the froth handling pump of the present invention is a conventional design for centrifugal slurry pumps; however, a modified, or more open inlet side may be contemplated for a particular froth handling application, or for alternative impeller configurations, as described below. Alternatively, as described in detail below, the front shroud may be eliminated in its entirety. - Referring to
FIGS. 2 through 5 , thenovel impeller 140 of thefroth handling pump 100 is illustrated in detail. As best shown inFIG. 3 , one embodiment of theimpeller 140 comprises afront shroud 142, arear shroud 144, and a plurality of pumpingvanes 146. As shown inFIG. 3 , thefront shroud 142 is conventional for a centrifugal slurry pump; however, in an alternative embodiment, thefront shroud 142 also may be modified for a particular froth handling application and could include a more open configuration, having a larger suction inlet diameter. As shown inFIG. 4 , theimpeller 140 of this illustrated embodiment comprises anovel pumping vane 146 arrangement. To maximize the number of pumpingvanes 146, as shown inFIG. 4 ,full size vanes 146 a andsplitter vanes 146 b are arranged in an alternating fashion about the circumference of theimpeller 140.Splitter vanes 146 b, as used herein and as shown in the Figures, are shorter, thus not extending radially inwardly as far toward thesuction eye 147 as the fullersize pumping vanes 146 a. As will be appreciated by those skilled in the pump art, the number of pumpingvanes splitter vanes 146 b helps to increase the effective number of pumpingvanes 146 without “choking” thesuction eye 147 of the impeller. - For froth handling applications, it has been found that a minimum passage size of about two inches is sufficient. As used herein, “passage size” refers to the minimum mid-channel clearance between two adjacent pumping vanes 146. As best shown in
FIG. 3 , the pumpingvane 146 geometry extends between the front 142 shroud (when included) and rear 144 shroud of theimpeller 140 in a manner that provides maximum efficiency. The inventors have found that the size of theimpeller 140, and thus the overall size of thepump 100, can be minimized by employing pumpingvanes 146 that have a combination of high angle outlets, for maximum head, and conventional lower angle inlets for developing sufficient NPSH performance. In the exemplary embodiments shown and described herein, an outlet vane angle may be between about 80 degrees and 100 degrees, with 90 degrees being optimal. As used herein, pumpingvane 146 angles are defined relative to the tangent of the impeller circumference; e.g., an outlet angle of 0 degrees would be tangential to the circumference of the impeller, while an outlet angle of 90 degrees is radial with respect to the center of the impeller, or perpendicular to the tangent of the impeller. - While the exemplary embodiments shown herein comprise an arrangement of 12 alternating
full size 146 a andsplitter 146 b pumping vanes, other pumping vane configurations also may provide suitable head and pumping efficiencies. For the pumpingvane 146 configuration, as shown, having outlet angles of about 90 degrees, the inventors have found unexpectedly that a relative efficiency of at least about 73 percent may be achieved when pumping clear water. - As further shown in
FIG. 4 , a plurality of vent holes 148 are formed through therear shroud 144 of theimpeller 140. The vent holes 148 are located for the effective venting of gases therethrough. For the bitumen application, for example, the vent holes 148 must provide a minimum opening of about 2 inches in diameter, or, if not circular, an area of about 3.14 square inches. - Turning now to
FIG. 5 , the principle of operation of the novelfroth handling pump 100 is schematically illustrated. As will be appreciated by those skilled in the art, when pumping a two-phase (gas and liquid, such as froth) flow, due to the centrifugal forces within the impeller, the gas (shown as G inFIG. 5 ) separates from the liquid at the inlet of the impeller. This causes the gas to accumulate on the trailing faces of theimpeller pumping vanes 146. As will also be appreciated, the continuous accumulation of gas during operation of the pump will eventually create “choking” of the impeller passage, resulting in cavitation and air lock of the impeller. - By providing
vent holes 148, as shown inFIG. 6 , at the appropriate circumferential locations through therear shroud 144 of theimpeller 140, the gases have outlets to escape from the impeller main passages. The size, shape, and relative positions of these vent holes 148 are influenced by the quantity and anticipated location for gas accumulation. In the illustrated embodiments shown in the Figures, the positions of the vent holes 148 correspond approximately to the suction diameter of the impeller. - Although the vent holes 148 provide outlets for the gaseous phase to escape, the passage of the gases may be facilitated by creating a differential pressure between the main impeller passages and the
outer face 144 a of therear shroud 144. Accordingly, and as shown inFIG. 6 , the present invention comprises animpeller 140 having a plurality of clearingvanes outer face 144 a of therear shroud 144. These clearing vanes serve several purposes: (1) they assist in balancing the axial thrust of the rotating impeller, and (2) they exert a static pressure equal to or greater than the main impeller vanes to restrict the inwardly entry of main (liquid) flow from the impeller outlet. Additionally, theclearing vanes clearing vanes outer face 144 a that is lower than the pressure in theimpeller suction eye 147. By creating this differential pressure, the gases are drawn through the impeller vent holes 148 into the attachedde-aeration chamber 160. As shown inFIG. 6 , theclearing vanes outer face 144 a of therear shroud 144. In the embodiment shown, there are 18clearing vanes short vanes 149 a and 6long vanes 149 b; however, the total number of clearing vanes is not critical to the operation of thefroth handling pump 100 of the present invention. Rather, the number, geometry, and angles of the clearing vanes are dependent upon the particular froth handling application. By forming the clearing vanes in the manner shown inFIG. 6 , i.e., with short and long vanes, the number ofclearing vanes clearing vanes vanes 146 by as much as 10 percent to obtain the desired pressure differential between theimpeller suction eye 147 and thede-aeration chamber 160. This means that theclearing vanes vanes 146. - In one embodiment, as shown in
FIG. 7 , anauxiliary impeller configuration 180 may be rigidly mounted on theouter face 144 a of therear shroud 144. The inventors have found that this configuration assists in creating a negative pressure relative to the pumping vanes 146. As shown inFIG. 7 , the outer radius of theauxiliary impeller configuration 180 is greater than the maximum radial position of the vent holes 148 to prevent gases from being trapped on theouter face 144 a. - Turning now to
FIGS. 8 and 9 , thede-aeration chamber 160 is illustrated. As shown in the Figures, thede-aeration chamber 160 has aninlet opening 162 having a diameter that is dimensioned to extend outwardly beyond the maximum radial position of the vent holes 148 in therear shroud 144. The de-aeration chamber is thus rigidly coupled to therear side 124 of thepump casing 120 by bolting or other conventional fastening means. As will be appreciated, pump casing 120 is modified from a conventional centrifugal pump casing, with an opening formed in therear side 124 of thepump casing 120 corresponding in size to the inlet opening 162 of thede-aeration chamber 160. - As shown the Figures, the
de-aeration chamber 160 comprises ahousing 163 having an inner volume. As shown, thede-aeration chamber 160 is a passive component of thefroth handling pump 100 construction; i.e., thechamber 160 has no moving or movable parts. As best shown inFIGS. 2 and 9 , anopening 165 is formed on therear face 164 of thede-aeration chamber 160 for passage of the to pumpshaft 170 therethrough thechamber 160 for mounting to theimpeller hub 142. At least oneoutlet 166 is formed for discharging the gases from thechamber 160. Depending on the particular froth handling application, thede-aeration chamber 160 may comprise asecond outlet 168. For bitumen froth handling, for example, it has been found that theoutlets outlet 166 should be located at about 22.5 degrees or less of vertical (in either direction from the vertical) for sufficiently releasing the gases. Theoutlet 166 may be provided with aflange 167 so that it may be interconnected to a discharge line (not shown) leading to a location suitable for discharging the vented gases. As will be understood, the vented flow may include some liquid discharge that should be diverted to a sump or other drainage location. Further,outlet 168 may be utilized for cleaning and drainage, as necessary. - Turning now to
FIGS. 10 and 11 , an alternative embodiment of thenovel impeller 240 of thefroth pump 100 of the present invention is shown. As shown inFIG. 10 , the impeller is an open-shroud configuration, comprising only arear shroud 244 and a plurality of pumpingvanes 246, includingfull size vanes 146 a andsplitter vanes 146 b. In this embodiment, with elimination of a front shroud, the pumpingvanes 246 may be geometrically extrapolated outwardly axially toward the suction liner to compensate for the thickness of a front shroud. The inventors again have found that an outlet vane angle may be between about 80 degrees and 100 degrees, with 90 degrees being optimal. In all other respects, the configuration of thepump 100, including thede-aeration chamber 160, are similar to the closed-shroud configuration of thepump 100. - It is believed that the open-shroud configuration creates greater shear and turbulence between the pumping vanes and the suction liner of the pump, which breaks up air bubbles and further delays the formation of an air lock bubble. The inventors have found that this effectively increases the suction diameter, which reduces the velocity at the inlet edge of the impeller, and thereby increases the static pressure at the inlet edge. Optionally, the diameter of the suction inlet of the
pump casing 120 may be increased for the open-shroud impeller to provide more open suction, which is less subject to air blockage. This effectively reduces the velocity at the inlet edge of the impeller, and thereby increases the static pressure there, which delays vapor formation (cavitation). - Turning lastly to
FIGS. 12 and 13 , testing and performance data for both embodiments of thepump 100 are graphically illustrated. The testing was performed under similar conditions for both embodiments. A water-soap froth was formulated for the testing of the novel impellers.FIGS. 12 and 13 demonstrate the is performance of the open-shroud froth handling impeller compared to the closed-shroud embodiment described herein. Data is provided with the venting system open and closed, and at two different flowrates above and below the pump design flowrate. The open-shroud froth impeller resists air lock at a higher percentage of air than the closed-shroud froth impeller. The open-shroud froth impeller also exhibits a lower degree of losses than the closed-shroud design after air lock, with the venting system operational. - Although the present invention has been described with exemplary embodiments, it is to be understood that modifications and variations may be utilized without departing from the spirit and scope of the invention, as those skilled in the art will readily understand. Such modifications and variations are considered to be within the purview and scope of the appended claims and their equivalents.
Claims (21)
1. A froth handling pump, comprising
(a) a pump casing having an inlet side and a rear side;
(b) an impeller mounted within the casing, the impeller comprising:
(i) a rear shroud, comprising:
(A) an inner face and an outer face;
(B) a plurality of vent holes formed through the rear shroud for the passage of gases therethrough;
(ii) a plurality of pumping vanes, each of the pumping vanes comprising:
(A) inlet ends affixed to the inner face of the rear shroud and extending radially inwardly from the rear shroud;
(B) an inlet angle and an outlet angle, wherein the outlet is angle is greater than the inlet angle, the outlet angles terminating at the rear shroud;
(c) a de-aeration chamber mounted to the rear side of the pump casing and comprising:
(i) an inner volume;
(ii) an inner side mounted to the rear side of the pump casing;
(iii) an inlet formed on the inner side for receiving gases passing through the plurality of vent holes; and
(iv) at least one vent outlet for the discharge of gases therethrough.
2. The pump of claim 1 , wherein the plurality of pumping vanes extending radially inwardly from the rear shroud terminate at free ends.
3. The pump of claim 2 , wherein the space between the free ends of the pumping vanes and the inlet side of the pump casing being free of a front shroud;
4. The pump of claim 1 , wherein the outlet angles of the pumping vanes are between about 80 degrees and about 100 degrees.
5. The pump of claim 4 , wherein the outlet angles of the pumping vanes are about 90 degrees.
6. The pump of claim 1 , wherein the pumping vanes comprise full size main pumping vanes, and splitter vanes of a lesser radial dimension.
7. The pump of claim 6 , wherein the impeller comprises 12 pumping vanes comprising:
(a) 6 main pumping vanes;
(b) 6 splitter vanes; and
wherein the pumping vanes and splitter vanes are arranged in an alternating configuration, having passages therebetween.
8. The pump of claim 1 , wherein the passage size between adjacent pumping vanes is at least about 2 inches.
9. The pump of claim 1 , further comprising a plurality of clearing vanes formed on the outer face of the rear shroud.
10. The pump of claim 9 , wherein the plurality of clearing vanes are configured to create a pressure on the outer face of the rear shroud less than the pressure created by the pumping vanes.
11. The pump of claim 10 , wherein the clearing vanes project outwardly from the outer face of the rear shroud at about a 90 degree angle.
12. The pump of claim 11 , wherein the rear shroud has a central hub and wherein the clearing vanes have differing lengths extending radially outwardly relative to the central hub.
13. The pump of claim 9 , wherein the clearing vanes are at least about 5 percent larger in diameter than the pumping vanes.
14. The pump of claim 1 , wherein the vent holes in the rear shroud each have a minimum area of at least about 3.14 square inches.
15. The pump of claim 1 , wherein the at least one vent outlet on the de-aeration chamber is positioned at an angle of less than about 45 degrees with respect to the vertical.
16. The pump of claim 15 , wherein the at least one vent outlet is positioned at an angle of about 22.5 degrees with respect to the vertical.
17. The pump of claim 1 , wherein the at least one vent outlet has an outlet diameter of at least about 3 inches.
18. The pump of claim 1 , where the de-aeration chamber further comprises a drain outlet.
19. The pump of claim 1 , further comprising an auxiliary impeller mounted to the outer face of the rear shroud.
20. The pump of claim 19 , wherein the auxiliary impeller has an outer radius that is greater than the maximum radial position of the plurality of vent holes.
21. The pump of claim 1 , wherein the impeller comprises a front shroud.
Priority Applications (11)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US12/543,303 US20100061841A1 (en) | 2008-09-11 | 2009-08-18 | Froth handling pump |
BRPI0918015A BRPI0918015A2 (en) | 2008-09-11 | 2009-09-11 | foam handling pump |
RU2011113962/05A RU2011113962A (en) | 2008-09-11 | 2009-09-11 | FLOTATION FOAM PUMP |
CA2732683A CA2732683A1 (en) | 2008-09-11 | 2009-09-11 | Froth handling pump |
EP09813648A EP2331227A4 (en) | 2008-09-11 | 2009-09-11 | Froth handling pump |
MX2011002615A MX2011002615A (en) | 2008-09-11 | 2009-09-11 | Froth handling pump. |
PCT/US2009/056603 WO2010030841A1 (en) | 2008-09-11 | 2009-09-11 | Froth handling pump |
PE2011000149A PE20110790A1 (en) | 2008-09-11 | 2009-09-11 | FOAM HANDLING PUMP |
AU2009291679A AU2009291679A1 (en) | 2008-09-11 | 2009-09-11 | Froth handling pump |
ZA2011/01013A ZA201101013B (en) | 2008-09-11 | 2011-02-08 | Froth handling pump |
CL2011000316A CL2011000316A1 (en) | 2008-09-11 | 2011-02-14 | Foam handling pump, comprising a housing, an impeller mounted inside the housing, said impeller comprises a rear cover with an inner face and an outer face, a plurality of vent holes, and a plurality of pumping blades, a deaeration chamber on the back side of the housing. |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US12/208,747 US20100061849A1 (en) | 2008-09-11 | 2008-09-11 | Froth handling pump |
US12/543,303 US20100061841A1 (en) | 2008-09-11 | 2009-08-18 | Froth handling pump |
Related Parent Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US12/208,747 Continuation-In-Part US20100061849A1 (en) | 2008-09-11 | 2008-09-11 | Froth handling pump |
Publications (1)
Publication Number | Publication Date |
---|---|
US20100061841A1 true US20100061841A1 (en) | 2010-03-11 |
Family
ID=41799465
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US12/543,303 Abandoned US20100061841A1 (en) | 2008-09-11 | 2009-08-18 | Froth handling pump |
Country Status (11)
Country | Link |
---|---|
US (1) | US20100061841A1 (en) |
EP (1) | EP2331227A4 (en) |
AU (1) | AU2009291679A1 (en) |
BR (1) | BRPI0918015A2 (en) |
CA (1) | CA2732683A1 (en) |
CL (1) | CL2011000316A1 (en) |
MX (1) | MX2011002615A (en) |
PE (1) | PE20110790A1 (en) |
RU (1) | RU2011113962A (en) |
WO (1) | WO2010030841A1 (en) |
ZA (1) | ZA201101013B (en) |
Cited By (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2014176189A1 (en) * | 2013-04-23 | 2014-10-30 | Dresser-Rand Company | Impeller internal thermal cooling holes |
WO2016165795A1 (en) * | 2015-04-15 | 2016-10-20 | Sulzer Management Ag | An impeller for a centrifugal headbox feed pump |
WO2016193387A1 (en) * | 2015-06-03 | 2016-12-08 | Gea Tuchenhagen Gmbh | Impeller for a centrifugal pump, and centrifugal pump |
CN106359244A (en) * | 2016-11-18 | 2017-02-01 | 许海琴 | Diving aerator |
GB2554761A (en) * | 2016-10-10 | 2018-04-11 | Aspen Pumps Ltd | Pump impeller |
US11117107B2 (en) * | 2016-07-18 | 2021-09-14 | Cellmotions Inc. | Low shear, low velocity differential, impeller having a progressively tapered hub volume with periods formed into a bottom surface, systems and methods for suspension cell culturing |
CN114307259A (en) * | 2021-12-30 | 2022-04-12 | 中国航空工业集团公司金城南京机电液压工程研究中心 | Pump type oil-gas separator of hydraulic combined transmission generator |
Families Citing this family (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
RU2542078C1 (en) * | 2014-01-31 | 2015-02-20 | Совместное предприятие в форме Закрытого акционерного общества "Изготовление, Внедрение, Сервис" (СП ЗАО "ИВС") | Transfer device of froth product of flotation stage |
RU2547872C1 (en) * | 2014-03-18 | 2015-04-10 | Совместное предприятие в форме Закрытого акционерного общества "Изготовление, Внедрение, Сервис" (СП ЗАО "ИВС") | Device for pumping froth product of flotation processing |
Citations (18)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3414245A (en) * | 1965-05-07 | 1968-12-03 | Frazer David | Froth flotation apparatus or pump device |
US3671135A (en) * | 1970-05-15 | 1972-06-20 | Warman Equipment Intern Ltd | Froth pump |
US4116809A (en) * | 1976-04-27 | 1978-09-26 | Her Majesty The Queen In Right Of Canada, As Represented By The Minister Of Energy, Mines And Resources | Deaerator circuit for bitumen froth |
US4170797A (en) * | 1976-07-23 | 1979-10-16 | Sundberg Hardy M | Apparatus for treating waste matter |
US4331458A (en) * | 1977-12-30 | 1982-05-25 | Smith International, Inc. | Degassing system and centrifugal pump |
US4474530A (en) * | 1982-04-21 | 1984-10-02 | General Electric Company | Method and apparatus for degrading antimisting fuel |
US4936744A (en) * | 1989-07-25 | 1990-06-26 | Goulds Pumps, Incorporated | Centrifugal pump |
US5143525A (en) * | 1990-06-29 | 1992-09-01 | Chemap Ag | Process and apparatus for breaking up foam into its liquid and gaseous components |
US5152663A (en) * | 1990-09-07 | 1992-10-06 | A. Ahlstrom Corporation | Centrifugal pump |
US5167678A (en) * | 1988-04-11 | 1992-12-01 | A. Ahlstrom Corporation | Apparatus for separating gas with a pump from a medium being pumped |
US5939122A (en) * | 1996-09-23 | 1999-08-17 | Brady; Frank A. | Method for frothing liquids |
US6007708A (en) * | 1997-10-02 | 1999-12-28 | Alberta Energy Company Ltd. | Cold dense slurrying process for extracting bitumen from oil sand |
US6190121B1 (en) * | 1999-02-12 | 2001-02-20 | Hayward Gordon Limited | Centrifugal pump with solids cutting action |
US6391190B1 (en) * | 1999-03-04 | 2002-05-21 | Aec Oil Sands, L.P. | Mechanical deaeration of bituminous froth |
US6619910B1 (en) * | 1998-12-04 | 2003-09-16 | Warman International Limited | Froth pumps |
US6800116B2 (en) * | 2002-05-23 | 2004-10-05 | Suncor Energy Inc. | Static deaeration conditioner for processing of bitumen froth |
US20080213093A1 (en) * | 2003-08-04 | 2008-09-04 | Sulzer Pumpen Ag | Impeller for Pumps |
US7475628B2 (en) * | 2003-05-02 | 2009-01-13 | M. Schaerer Ag | Device for dispensing milk and/or milk froth |
Family Cites Families (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DD101947A1 (en) * | 1972-12-28 | 1973-11-20 | ||
SE467466B (en) * | 1989-03-29 | 1992-07-20 | Kamyr Ab | DEVICE FOR FLUIDIZATION, GAS SEPARATION AND PUMPING OF A SUSPENSION OF FIBER-containing CELLULO MATERIAL, AND ITS APPLICATION |
CA2120977A1 (en) | 1994-04-11 | 1995-10-12 | Baha Elsayed Abulnaga | Impeller with alternating primary and secondary vanes of different geometries |
-
2009
- 2009-08-18 US US12/543,303 patent/US20100061841A1/en not_active Abandoned
- 2009-09-11 RU RU2011113962/05A patent/RU2011113962A/en unknown
- 2009-09-11 MX MX2011002615A patent/MX2011002615A/en not_active Application Discontinuation
- 2009-09-11 PE PE2011000149A patent/PE20110790A1/en not_active Application Discontinuation
- 2009-09-11 CA CA2732683A patent/CA2732683A1/en not_active Abandoned
- 2009-09-11 AU AU2009291679A patent/AU2009291679A1/en not_active Abandoned
- 2009-09-11 WO PCT/US2009/056603 patent/WO2010030841A1/en active Application Filing
- 2009-09-11 BR BRPI0918015A patent/BRPI0918015A2/en not_active IP Right Cessation
- 2009-09-11 EP EP09813648A patent/EP2331227A4/en not_active Withdrawn
-
2011
- 2011-02-08 ZA ZA2011/01013A patent/ZA201101013B/en unknown
- 2011-02-14 CL CL2011000316A patent/CL2011000316A1/en unknown
Patent Citations (18)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3414245A (en) * | 1965-05-07 | 1968-12-03 | Frazer David | Froth flotation apparatus or pump device |
US3671135A (en) * | 1970-05-15 | 1972-06-20 | Warman Equipment Intern Ltd | Froth pump |
US4116809A (en) * | 1976-04-27 | 1978-09-26 | Her Majesty The Queen In Right Of Canada, As Represented By The Minister Of Energy, Mines And Resources | Deaerator circuit for bitumen froth |
US4170797A (en) * | 1976-07-23 | 1979-10-16 | Sundberg Hardy M | Apparatus for treating waste matter |
US4331458A (en) * | 1977-12-30 | 1982-05-25 | Smith International, Inc. | Degassing system and centrifugal pump |
US4474530A (en) * | 1982-04-21 | 1984-10-02 | General Electric Company | Method and apparatus for degrading antimisting fuel |
US5167678A (en) * | 1988-04-11 | 1992-12-01 | A. Ahlstrom Corporation | Apparatus for separating gas with a pump from a medium being pumped |
US4936744A (en) * | 1989-07-25 | 1990-06-26 | Goulds Pumps, Incorporated | Centrifugal pump |
US5143525A (en) * | 1990-06-29 | 1992-09-01 | Chemap Ag | Process and apparatus for breaking up foam into its liquid and gaseous components |
US5152663A (en) * | 1990-09-07 | 1992-10-06 | A. Ahlstrom Corporation | Centrifugal pump |
US5939122A (en) * | 1996-09-23 | 1999-08-17 | Brady; Frank A. | Method for frothing liquids |
US6007708A (en) * | 1997-10-02 | 1999-12-28 | Alberta Energy Company Ltd. | Cold dense slurrying process for extracting bitumen from oil sand |
US6619910B1 (en) * | 1998-12-04 | 2003-09-16 | Warman International Limited | Froth pumps |
US6190121B1 (en) * | 1999-02-12 | 2001-02-20 | Hayward Gordon Limited | Centrifugal pump with solids cutting action |
US6391190B1 (en) * | 1999-03-04 | 2002-05-21 | Aec Oil Sands, L.P. | Mechanical deaeration of bituminous froth |
US6800116B2 (en) * | 2002-05-23 | 2004-10-05 | Suncor Energy Inc. | Static deaeration conditioner for processing of bitumen froth |
US7475628B2 (en) * | 2003-05-02 | 2009-01-13 | M. Schaerer Ag | Device for dispensing milk and/or milk froth |
US20080213093A1 (en) * | 2003-08-04 | 2008-09-04 | Sulzer Pumpen Ag | Impeller for Pumps |
Cited By (12)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2014176189A1 (en) * | 2013-04-23 | 2014-10-30 | Dresser-Rand Company | Impeller internal thermal cooling holes |
US9568016B2 (en) | 2013-04-23 | 2017-02-14 | Dresser-Rand Company | Impeller internal thermal cooling holes |
WO2016165795A1 (en) * | 2015-04-15 | 2016-10-20 | Sulzer Management Ag | An impeller for a centrifugal headbox feed pump |
CN107429698A (en) * | 2015-04-15 | 2017-12-01 | 苏尔寿管理有限公司 | For centrifuging the impeller of head box supply pump |
US10247195B2 (en) | 2015-04-15 | 2019-04-02 | Sulzer Management Ag | Impeller for a centrifugal headbox feed pump |
WO2016193387A1 (en) * | 2015-06-03 | 2016-12-08 | Gea Tuchenhagen Gmbh | Impeller for a centrifugal pump, and centrifugal pump |
CN107995939A (en) * | 2015-06-03 | 2018-05-04 | 基伊埃图亨哈根有限公司 | Active wheel and centrifugal pump for centrifugal pump |
DE102016110224B4 (en) * | 2015-06-03 | 2020-03-12 | Gea Tuchenhagen Gmbh | Centrifugal pump and impeller for a centrifugal pump |
US11117107B2 (en) * | 2016-07-18 | 2021-09-14 | Cellmotions Inc. | Low shear, low velocity differential, impeller having a progressively tapered hub volume with periods formed into a bottom surface, systems and methods for suspension cell culturing |
GB2554761A (en) * | 2016-10-10 | 2018-04-11 | Aspen Pumps Ltd | Pump impeller |
CN106359244A (en) * | 2016-11-18 | 2017-02-01 | 许海琴 | Diving aerator |
CN114307259A (en) * | 2021-12-30 | 2022-04-12 | 中国航空工业集团公司金城南京机电液压工程研究中心 | Pump type oil-gas separator of hydraulic combined transmission generator |
Also Published As
Publication number | Publication date |
---|---|
CA2732683A1 (en) | 2010-03-18 |
CL2011000316A1 (en) | 2011-06-03 |
BRPI0918015A2 (en) | 2015-11-17 |
AU2009291679A1 (en) | 2010-03-18 |
ZA201101013B (en) | 2012-07-25 |
PE20110790A1 (en) | 2011-11-23 |
EP2331227A1 (en) | 2011-06-15 |
WO2010030841A1 (en) | 2010-03-18 |
MX2011002615A (en) | 2011-04-07 |
EP2331227A4 (en) | 2012-04-25 |
RU2011113962A (en) | 2012-10-20 |
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