EP2331227A1 - Pompe prenant en charge l'écume - Google Patents

Pompe prenant en charge l'écume

Info

Publication number
EP2331227A1
EP2331227A1 EP09813648A EP09813648A EP2331227A1 EP 2331227 A1 EP2331227 A1 EP 2331227A1 EP 09813648 A EP09813648 A EP 09813648A EP 09813648 A EP09813648 A EP 09813648A EP 2331227 A1 EP2331227 A1 EP 2331227A1
Authority
EP
European Patent Office
Prior art keywords
pump
vanes
impeller
outlet
shroud
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP09813648A
Other languages
German (de)
English (en)
Other versions
EP2331227A4 (fr
Inventor
Robert J. Visintainer
Peter Hergt
Thillainatarajan Ravisundar
Christoph Jaeger
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
GIW Industries Inc
Original Assignee
GIW Industries Inc
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from US12/208,747 external-priority patent/US20100061849A1/en
Application filed by GIW Industries Inc filed Critical GIW Industries Inc
Publication of EP2331227A1 publication Critical patent/EP2331227A1/fr
Publication of EP2331227A4 publication Critical patent/EP2331227A4/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • 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
    • 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
    • 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 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.
  • 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).
  • 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.
  • Figure 1 is a perspective view of an embodiment of the froth handling pump of the present invention.
  • Figure 2 is a side elevational cross-sectional view of the froth handling pump of Figure 1.
  • Figure 3 is a perspective view of one embodiment of the impeller of the froth handling pump of Figure 1.
  • Figure 4 is a front view of the impeller of Figure 3 with the front shroud removed to show the vanes.
  • Figure 5 is a schematic illustration of the gaseous venting scheme of the froth handling pump of Figure 1.
  • Figure 6 is a side rear view of the shroud of the impeller of Figure 3, illustrating the arrangement and geometry of the clearing vanes.
  • Figure 7 is a rear perspective view illustrating the optional auxiliary impeller on the rear shroud of the impeller of Figure 3.
  • Figure 8 is a perspective view of the de-aeration chamber of the froth handling pump of Figure 1.
  • Figure 9 is a side rear view of the de-aeration chamber of Figure 8.
  • Figure 10 is a perspective view of an alternative embodiment of the impeller of the froth handling pump of Figure 1.
  • Figure 11 is a front view of the impeller of Figure 10.
  • Figure 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.
  • Figure 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.
  • the front shroud may be eliminated in its entirety.
  • the novel impeller 140 of the froth handling pump 100 is illustrated in detail. As best shown in Figure 3, 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. To maximize the number of pumping vanes 146, as shown in Figure 4, full size vanes 146a and splitter vanes 146b are arranged in an alternating fashion about the circumference of the impeller 140.
  • Splitter vanes 146b are shorter, thus not extending radially inwardly as far toward the suction eye 147 as the fuller size pumping vanes 146a.
  • the number of pumping vanes 146a, 146b is maximized within the constraints of vane thickness and minimum required passage size. It has been found, however, that the use of splitter vanes 146b 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
  • 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.
  • vent holes 148 By providing vent holes 148, as shown in Figure 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 149a, 149b formed on the outer face 144a 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 149a and 149b are formed such that, as the impeller rotates, the clearing vanes 149a, 149b create a pressure at the outer face 144a 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 Figure 6, the clearing vanes 149a, 149b are radially-oriented (90 degrees) and extend substantially perpendicularly outward from the outer face 144a of the rear shroud 144.
  • clearing vanes 149a, 149b there are 18 clearing vanes 149a, 149b, comprising 12 short vanes 149a and 6 long vanes 149b; 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. By forming the clearing vanes in the manner shown in Figure 6, i.e., with short and long vanes, the number of clearing vanes 149a, 149b may be maximized.
  • the clearing vanes 149a, 149b 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. This means that the clearing vanes 149a, 149b extend radially inwardly further than the pumping vanes 146.
  • an auxiliary impeller configuration 180 may be rigidly mounted on the outer face 144a of the rear shroud 144. The inventors have found that this configuration assists in creating a negative pressure relative to the pumping vanes 146. As shown in Figure 7, 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 144a. Turning now to Figures 8 and 9, the de-aeration chamber 160 is illustrated.
  • 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 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.
  • the 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 146a and splitter vanes 146b.
  • 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. 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.
  • 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).
  • FIG. 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.
  • Figures 12 and 13 demonstrate the 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.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

L'invention porte sur une pompe prenant en charge l'écume comprenant un corps de pompe, une roue montée à l'intérieur du corps et une chambre de désaération montée sur le côté arrière du corps de pompe. La roue comprend de multiples ailettes de pompage, chacune des ailettes ayant un angle d'entrée et un angle de sortie, l'angle de sortie étant supérieur à l'angle d'entrée, les angles de sortie se terminant au niveau d'un flasque arrière. Le flasque arrière comprend de multiples évents pour le passage de gaz à travers ceux-ci. La chambre de désaération, qui comprend un volume interne, comprend une entrée formée du côté interne pour recevoir des gaz passant dans la pluralité d'évents. Au moins une sortie d'évent est pourvue pour l'évacuation des gaz de la chambre de désaération.
EP09813648A 2008-09-11 2009-09-11 Pompe prenant en charge l'écume Withdrawn EP2331227A4 (fr)

Applications Claiming Priority (3)

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
PCT/US2009/056603 WO2010030841A1 (fr) 2008-09-11 2009-09-11 Pompe prenant en charge l'écume

Publications (2)

Publication Number Publication Date
EP2331227A1 true EP2331227A1 (fr) 2011-06-15
EP2331227A4 EP2331227A4 (fr) 2012-04-25

Family

ID=41799465

Family Applications (1)

Application Number Title Priority Date Filing Date
EP09813648A Withdrawn EP2331227A4 (fr) 2008-09-11 2009-09-11 Pompe prenant en charge l'écume

Country Status (11)

Country Link
US (1) US20100061841A1 (fr)
EP (1) EP2331227A4 (fr)
AU (1) AU2009291679A1 (fr)
BR (1) BRPI0918015A2 (fr)
CA (1) CA2732683A1 (fr)
CL (1) CL2011000316A1 (fr)
MX (1) MX2011002615A (fr)
PE (1) PE20110790A1 (fr)
RU (1) RU2011113962A (fr)
WO (1) WO2010030841A1 (fr)
ZA (1) ZA201101013B (fr)

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9568016B2 (en) 2013-04-23 2017-02-14 Dresser-Rand Company Impeller internal thermal cooling holes
RU2542078C1 (ru) * 2014-01-31 2015-02-20 Совместное предприятие в форме Закрытого акционерного общества "Изготовление, Внедрение, Сервис" (СП ЗАО "ИВС") Устройство для перекачки пенного продукта флотационного передела
RU2547872C1 (ru) * 2014-03-18 2015-04-10 Совместное предприятие в форме Закрытого акционерного общества "Изготовление, Внедрение, Сервис" (СП ЗАО "ИВС") Устройство для перекачки пенного продукта флотационного передела
CN107429698B (zh) * 2015-04-15 2021-01-08 苏尔寿管理有限公司 用于离心流浆箱供给泵的叶轮
ES2756602T3 (es) * 2015-06-03 2020-04-27 Gea Tuchenhagen Gmbh Rodete para una bomba centrífuga y bomba centrífuga
CA2936339C (fr) * 2016-07-18 2019-02-12 Carl R. Bachellier Roue a ailettes ayant une faible vitesse differentielle et un faible cisaillement offrant un volume de moyeu a profil progressif periodique forme sur une surface de fond
GB2554761A (en) * 2016-10-10 2018-04-11 Aspen Pumps Ltd Pump impeller
CN106359244B (zh) * 2016-11-18 2022-06-21 许海琴 一种潜水增氧机
CN114307259B (zh) * 2021-12-30 2023-05-30 中国航空工业集团公司金城南京机电液压工程研究中心 一种液力式组合传动发电机的泵式油气分离器

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CA2120977A1 (fr) 1994-04-11 1995-10-12 Baha Elsayed Abulnaga Turbine avec aubages primaire et secondaire de geometries differentes

Family Cites Families (20)

* Cited by examiner, † Cited by third party
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
DD101947A1 (fr) * 1972-12-28 1973-11-20
CA1072474A (fr) * 1976-04-27 1980-02-26 Imperial Oil Limited Desaerateur de mousse bitumineuse
SE402450B (sv) * 1976-07-23 1978-07-03 Sundberg Hardy Mikael Sett for behandling av avfallsmaterial i formultningsanordningar samt anordning for genomforande av settet
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
SE467466B (sv) * 1989-03-29 1992-07-20 Kamyr Ab Apparat foer fluidisering, gasavskiljning och pumpning av en suspension av fiberhaltigt cellulosamaterial, samt dess anvaendning
US4936744A (en) * 1989-07-25 1990-06-26 Goulds Pumps, Incorporated Centrifugal pump
DE4020645A1 (de) * 1990-06-29 1992-01-09 Chemap Ag Verfahren und apparat zur zerlegung von schaum
US5152663A (en) * 1990-09-07 1992-10-06 A. Ahlstrom Corporation Centrifugal pump
US5780087A (en) * 1996-09-23 1998-07-14 Brady; Frank A. Apparatus and method for frothing liquids
CA2217623C (fr) * 1997-10-02 2001-08-07 Robert Siy Procede d'extraction du bitume des sables bitumineux en suspension epaisse froide
AUPP750898A0 (en) * 1998-12-04 1999-01-07 Warman International Limited Impeller relating to 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
CA2387257C (fr) * 2002-05-23 2009-07-28 Suncor Energy Inc. Conditionneur fixe de desaeration pour le traitement de la mousse de bitume
EP1472963B1 (fr) * 2003-05-02 2008-12-10 M. Schaerer AG Dispositif pour distribuer du lait et/ou de la mousse de lait
CN100449155C (zh) * 2003-08-04 2009-01-07 苏舍泵有限公司 用于泵的叶轮、包括这种叶轮的泵及其工作方法

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CA2120977A1 (fr) 1994-04-11 1995-10-12 Baha Elsayed Abulnaga Turbine avec aubages primaire et secondaire de geometries differentes

Non-Patent Citations (3)

* Cited by examiner, † Cited by third party
Title
ABULNAGA B.: "Pumping Oil Sand Froth", WORLD COAL, vol. 15, no. 2, February 2006 (2006-02-01), pages 1 - 9, XP003030353, Retrieved from the Internet <URL:www.worldcoal.com>
ABULNAGA B.E.: "Pumped Clean", 21ST INTERNATIONAL PUMP USERS SYMPOSIUM, March 2004 (2004-03-01), pages 33 - 34,36, XP003030352, Retrieved from the Internet <URL:www.worldcoal.com>
See also references of WO2010030841A1

Also Published As

Publication number Publication date
US20100061841A1 (en) 2010-03-11
ZA201101013B (en) 2012-07-25
MX2011002615A (es) 2011-04-07
AU2009291679A1 (en) 2010-03-18
CL2011000316A1 (es) 2011-06-03
CA2732683A1 (fr) 2010-03-18
BRPI0918015A2 (pt) 2015-11-17
WO2010030841A1 (fr) 2010-03-18
EP2331227A4 (fr) 2012-04-25
PE20110790A1 (es) 2011-11-23
RU2011113962A (ru) 2012-10-20

Similar Documents

Publication Publication Date Title
US20100061841A1 (en) Froth handling pump
EP2427632B1 (fr) Pompe sous-marine supportant la presence de gaz
US9719523B2 (en) Apparatus, system and method for pumping gaseous fluid
US6361272B1 (en) Centrifugal submersible pump
US8568081B2 (en) Axial thrust balanced impeller for use with a downhole electrical submersible pump
US9624930B2 (en) Multiphase pumping system
US8141625B2 (en) Gas boost circulation system
US7461692B1 (en) Multi-stage gas separator
CA2557098C (fr) Conditionneur d&#39;ecoulement biphase pour le pompage de fluide gazeux dans des puits
US5516360A (en) Abrasion resistant gas separator
US10371154B2 (en) Apparatus, system and method for pumping gaseous fluid
US20100061849A1 (en) Froth handling pump
US9500202B1 (en) Thrust bearing surface for floater-style centrifugal pumps
US11643916B2 (en) Downhole pumping system with cyclonic solids separator
WO2005050024A1 (fr) Nombreux organes de derivation pour reduire l&#39;usure dans une pompe a boue
EP3312432B1 (fr) Diffuseur pour dispositif de compression de fluide, comprenant au moins une aube avec ouverture
EP3971422B1 (fr) Roue ouverte de pompe submersible conçue pour le pompage de liquide comprenant des matières abrasives et pompe submersible comprenant ladite roue
EP3657024B1 (fr) Pompe à phases multiples
Kanute Self‐priming centrifugal pumps: a primer
CN203214401U (zh) 卧式多级凝结泵
US20240175339A1 (en) High volume axial flow electric submersible pump (esp) pump stage
CA2389406C (fr) Pompe centrifuge submersible
CA2809956C (fr) Appareil, systeme et procede pour pomper un fluide gazeux
CA2185176C (fr) Pompe separatrice pour liquides visqueux
CA2831924C (fr) Appareil, systeme et procede pour pomper un fluide gazeux

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20110315

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO SE SI SK SM TR

AX Request for extension of the european patent

Extension state: AL BA RS

DAX Request for extension of the european patent (deleted)
TPAC Observations filed by third parties

Free format text: ORIGINAL CODE: EPIDOSNTIPA

A4 Supplementary search report drawn up and despatched

Effective date: 20120323

RIC1 Information provided on ipc code assigned before grant

Ipc: F04D 9/00 20060101ALI20120319BHEP

Ipc: B01D 19/00 20060101AFI20120319BHEP

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE APPLICATION IS DEEMED TO BE WITHDRAWN

18D Application deemed to be withdrawn

Effective date: 20121023