EP3536975B1 - Système et méthodologie pour faciliter le pompage de fluide - Google Patents

Système et méthodologie pour faciliter le pompage de fluide Download PDF

Info

Publication number
EP3536975B1
EP3536975B1 EP19160495.8A EP19160495A EP3536975B1 EP 3536975 B1 EP3536975 B1 EP 3536975B1 EP 19160495 A EP19160495 A EP 19160495A EP 3536975 B1 EP3536975 B1 EP 3536975B1
Authority
EP
European Patent Office
Prior art keywords
impeller
recited
axial length
wear ring
pump
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.)
Active
Application number
EP19160495.8A
Other languages
German (de)
English (en)
Other versions
EP3536975A1 (fr
Inventor
Knut Harald Klepsvik
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.)
OneSubsea IP UK Ltd
Original Assignee
OneSubsea IP UK Ltd
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
Family has litigation
First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=65685235&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=EP3536975(B1) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by OneSubsea IP UK Ltd filed Critical OneSubsea IP UK Ltd
Publication of EP3536975A1 publication Critical patent/EP3536975A1/fr
Application granted granted Critical
Publication of EP3536975B1 publication Critical patent/EP3536975B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

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
    • F04D29/181—Axial flow rotors
    • F04D29/183—Semi axial flow rotors
    • 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
    • F04D29/08—Sealings
    • F04D29/16—Sealings between pressure and suction sides
    • F04D29/165—Sealings between pressure and suction sides especially adapted for liquid pumps
    • F04D29/168—Sealings between pressure and suction sides especially adapted for liquid pumps of an axial flow wheel
    • 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
    • F04D29/08—Sealings
    • F04D29/16—Sealings between pressure and suction sides
    • F04D29/165—Sealings between pressure and suction sides especially adapted for liquid pumps
    • 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
    • F04D29/181—Axial flow rotors
    • 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
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/52—Casings; Connections of working fluid for axial pumps
    • F04D29/54—Fluid-guiding means, e.g. diffusers
    • 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
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
    • F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps
    • F04D29/668—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps damping or preventing mechanical vibrations
    • 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
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
    • F04D29/669—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for liquid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D3/00—Axial-flow pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D31/00—Pumping liquids and elastic fluids at the same time
    • 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
    • F04D29/02—Selection of particular materials
    • 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
    • F04D29/02—Selection of particular materials
    • F04D29/026—Selection of particular materials especially adapted for liquid pumps

Definitions

  • Multiphase pumps are used in a variety of pumping applications, including subsea pumping applications involving the movement of hydrocarbon fluids having a mixture of oil and gas.
  • open impellers provide open impeller blade tips which allow fluid to leak over the blade tips through a clearance at the blade tips. This blade tip clearance helps to mix the multiphase fluid but it also can be the origin of a fluid induced rotor dynamic instability particularly at high head generation. This induced instability is sometimes called the Thomas-Alford effect.
  • the present invention provides a system for moving fluid as defined in claims 1 to 10 and in a method as defined in claims 11 to 15.
  • a multiphase axial pump is provided with an impeller having a plurality of impeller blades.
  • the impeller blades have blade tips which extend over an axial length.
  • a wear ring is positioned along the blade tips to suppress fluid induced Alford effects and to add annular seal direct stiffness to the impeller and to thus provide rotor dynamic stability.
  • the axial length of the ring is limited relative to the axial length of the impeller blade tips to enable flow, e.g. leakage, across the blade tips in a manner which causes active phase mixing during pumping of a multiphase fluid.
  • the disclosure herein generally relates to a system and methodology for enhancing pumping capabilities.
  • the system and methodology facilitate operation of a multiphase axial pump of the type that may be used to pump hydrocarbon-based fluids having various mixtures of oil and gas.
  • the pump is provided with at least one impeller having a plurality of impeller blades.
  • the multiphase pump comprise a plurality of impellers rotatably mounted within a pump housing. The impellers are rotationally fixed to a shaft which is rotated to thus rotate the impellers.
  • the impeller blades have blade tips which extend over an axial length, as described in greater detail below.
  • the impellers may be combined with corresponding diffusers to establish a desired number of pump stages disposed in the pump housing.
  • the impellers are rotated with respect to the diffusers to effectively pump the fluid, e.g. the multiphase fluid.
  • fluid flows through the diffusers as it moves from one sequential impeller to the next until being discharged from the pump housing.
  • each impeller has an impeller hub which is rotationally fixed to the shaft.
  • the impeller blades extending radially outward from the impeller hub each have an impeller blade base affixed to the impeller hub and an impeller tip located radially outward from the impeller blade base.
  • a wear ring is positioned and affixed along the blade tips to suppress fluid induced Alford effects and to add annular seal direct stiffness to the impeller.
  • the ring effectively suppresses fluid induced instability to the impeller, thus providing rotor dynamic stability during pump operation.
  • the ring extends from blade tip to blade tip along the entire circumference of the impeller.
  • the ring may be constructed with breaks such that it extends along a portion of the impeller circumference.
  • the ring of a given impeller also has an axial length, however the ring axial length is limited relative to the axial length of the impeller blade tips. This reduced axial length relative to the blade tips enables flow, e.g. leakage, across the blade tips in a manner which ensures active phase mixing during pumping of a fluid, e.g. a multiphase fluid.
  • the ring axial length relative to the impeller blade tip axial length may vary depending on the parameters of a given application.
  • the axial length of the ring may be 80% or less of the axial length of the impeller blade tips, e.g. 15% to 80%.
  • the ring axial length may be 50% or less of the axial length of the impeller blade tips, e.g. 15% to 50%. In various applications, the wear ring axial length may be from 10% to 95% of the axial length of the impeller blade tips.
  • the ring provides rotor dynamic stiffness to the corresponding impeller so as to limit fluid instabilities in the impeller, the shaft, and the shaft bearings.
  • the impellers (or a desired number of the impellers) may be combined with corresponding rings to provide the desired stiffness so as to reduce undesirable fluid based instabilities, e.g. vibrations.
  • wear rings may be fixed along blade tips of helico axial impellers in multiphase pumps to reduce the fluid instabilities otherwise experienced by the impellers and the pump shaft.
  • the wear ring or rings may be constructed to reduce unstable viscosity effects and thus stabilize Lomakin effects while still allowing leakage past the blade tips to ensure sufficiently active phase mixing during pumping. It should be noted that instability may lead to a variety of unwanted vibrations in the impellers and/or shaft to which the impellers are mounted. For example, at operating conditions of low gas volume fractions and low flow rates with high differential pressures some synchronous, sub-synchronous, or super-synchronous vibrations can occur in both forward and backward modes. The vibrations can result from fluid induced de-stabilizing forces due to the Thomas-Alford effect. For example, such effects may occur in forward mode for pumping devices such as turbines and in both forward and backward modes for a variety of pumps, e.g. helico axial pumps.
  • a schematic illustration is provided of an example of a pump 20 for moving a fluid, as represented by arrows 22.
  • the fluid 22 is a multiphase fluid such as a hydrocarbon-based fluid containing oil and gas.
  • the pump 20 may be in the form of a helico axial pump.
  • the pump 20 may be in the form of a helico axial pump operated to move hydrocarbon-based fluid which is in the form of multiphase mixtures of oil and natural gas.
  • the pump 20 comprises a pump housing 24 and a shaft 26 rotatably mounted in the pump housing 24.
  • the shaft 26 may be rotatably mounted on bearings 28 positioned, for example, between the housing 24 and shaft 26.
  • a plurality of radial bearings 28 may be positioned along the shaft 26.
  • the pump 20 comprises at least one impeller 30 and at least one diffuser 32.
  • the pump 20 is constructed with a plurality of impellers 30 and a plurality of corresponding diffusers 32 arranged in stages 34 which may be referred to as compression stages.
  • the number of stages 34 may vary depending on the pumping parameters for a given application and may comprise at least 10 stages, and sometimes at least 15 stages.
  • the impellers 30 are mounted to shaft 26 for rotation with the shaft 26 during operation of pump 20.
  • the impellers 30 may be rotationally affixed to shaft 26 via engaged teeth, key and keyway arrangements, or other suitable mechanisms for rotationally affixing the impellers 30 to shaft 26.
  • the diffusers 32 may be mounted stationary with respect to pump housing 24 and may operate to direct fluid 22 from one sequential impeller 30 to the next.
  • the pump 20 also comprises a discharge opening 36 or a plurality of discharge openings 36 through which the fluid is discharged from the pump 20 after being pumped through stages 34.
  • the discharge opening(s) 36 may be arranged in various configurations and locations to direct the fluid 22 into a corresponding component, e.g. a corresponding flow line.
  • a ring 38 is positioned along the outer circumference of each impeller 30.
  • the ring 38 is in the form of a wear ring.
  • the ring 38 is constructed from a different material than other portions of the impeller 30.
  • the ring 38 may be constructed from a hardened steel, carbide based material, or other suitable wear resistant material. Other types of materials also may be selected for ring 38 to provide desired wear and/or operational characteristics different from those of the other impeller material.
  • the ring 38 provides stiffness to the corresponding impeller 30 so as to limit fluid instabilities in both the impeller 30 and the shaft 26.
  • the pump comprises multiple impellers 30, the full set of impellers 30 or a desired number of the impellers 30, e.g. a reduced number of the impellers 30, may be combined with corresponding rings 38 to provide the desired stiffness so as to reduce undesirable vibrations or other fluid instabilities.
  • each impeller 30 comprises an impeller hub 40 rotationally affixed to the shaft 26.
  • Each impeller 30 further comprises a plurality of impeller blades 42 extending radially outward from the impeller hub 40.
  • Each impeller blade 42 has an impeller blade base 44 and an impeller blade tip 46.
  • the impeller blade bases 44 may be integrally formed with the impeller hub 40 or otherwise affixed to the impeller hub 40.
  • the impeller blade tips 46 have an axial length 48 extending along an axis 50 of the pump 20.
  • the ring 38 also as an axial length 52, but the ring axial length 52 is shorter than the impeller blade tip axial length 48.
  • Each ring 38 is located along the impeller blade tips 46 of the corresponding impeller 30, as illustrated in Figure 1 .
  • the ring 38 extends around the entire circumference of the corresponding impeller 30, as illustrated in Figure 2 .
  • other embodiments may utilize rings 38 which extend along a portion (or portions) of the circumference of the corresponding impellers 30.
  • the axial length 52 (see, for example, Figures 1 and 3 ) of the rings 38 relative to the axial length 48 of the corresponding impeller blade tips 46 varies according to the parameters of a given pumping application.
  • the ring axial length 52 may be less than 80% of the axial length 48 of the corresponding impeller blade tips 46.
  • the ring axial length 52 may be in the range from 30% to 80% of the axial length 48 of the impeller blade tips 46. In other embodiments, however, the ring axial length 52 may be in the range from 30% to 50% of the axial length 48 of the corresponding impeller blade tips 46.
  • the wear ring 38 may be located at an inlet side of the impeller 30 as illustrated. However, the wear ring 38 also may be located at other axial positions and other positions along the blade tips 46 in some applications. For example, the wear ring 38 may be positioned along the impeller blade tips 46 at the impeller inlet side, the impeller outlet side, or at various positions therebetween.
  • the ratio of ring axial length 52 to impeller blade tip axial length 48 is selected based on the desired stiffening of the corresponding impeller 30 and the desired mixing of multiphase fluids for a given set of pumping conditions and parameters.
  • the desired mixing of multiphase fluids results from allowing leakage of fluid 22 past the impeller blade tips 46 to a gap 54, e.g. a clearance, between the impeller blade tips 46 and a surrounding housing.
  • the axially shorter ring 38 does not prevent flow of fluid in a radially outward direction past impeller blade tips 46 and into gap 54 (thus promoting mixing).
  • the surrounding housing may be an inside surface of pump housing 24, a portion of a corresponding diffuser 32 extending along the impeller 30, or another suitable housing.
  • the contact surface between the ring 38 and the impeller blade tips 46 may be a continuous fixed interphase or it may include bores, slots, and/or other features to provide for fluid flow and mixing through the bores, slots, and/or other features.
  • the leakage or flow of fluid through gap 54 past the impeller blade tips 46 ensures sufficiently active phase mixing during pumping.
  • this flow past the impeller blade tips 46 and resultant mixing is allowed to occur.
  • the reduced axial length 52 of ring 38 stiffens the impeller while still enabling substantial mixing of multiphase fluids to ensure, for example, stable performance of the impellers 30 even with high viscosity fluids 22.
  • each ring 38 is able to reduce or eliminate unstable Bernoulli effects and thus reduce unstable cross coupled stiffness.
  • each ring 38 may be positioned along the corresponding impeller 30 to allow for blade tip flow at a latter part (downstream part) of the impeller blade tips 46 to provide the desired, active phase mixing.
  • the differential pressure acting on each impeller 30 is mainly created for the first half of the impeller 30. By positioning the ring 38 along the first half of the corresponding impeller 30, the ring 30 is exposed to the higher differential pressures, thus improving stabilization of the Lomakin effect.
  • ring 38 is in the form of a wear ring which extends radially outwardly of the impeller blade tips 46.
  • the wear ring 38 may be received in a corresponding slot 56 formed in a surrounding housing 58.
  • the surrounding housing 58 may be a portion of the corresponding diffuser 32 as illustrated in Figure 3 .
  • the surrounding housing 58 also may be a portion of pump housing 24 or part of another component of pump 20.
  • the wear ring 38 may be integrally formed with impeller blades 42. However, the wear ring 38 also may be a separate component affixed to the impeller blade tips 46 of the impeller blades 42. By way of example, the wear ring 38 may be affixed to impeller blades 42 via brazing, welding, adhesive, or other suitable fastening technique. The fastening technique also may depend on the similarity or dissimilarity of the materials used to form the wear ring 38 and the impeller blades 42. Additionally, the contact surface between the ring 38 and the impeller blade tips 46 may be a continuous fixed interphase or it may include features 60, e.g. bores or slots, to provide for fluid flow and mixing through the features 60.
  • the ring 38 is in the form of a wear ring.
  • the wear ring 38 is radially coextensive with the impeller blade tips 46.
  • the radially outlying surface of the wear ring 38 does not extend radially outwardly of the impeller tips 46.
  • gap 54 remains between the impeller blade tips 46 and the surrounding housing 58 along a portion of the axial length 48 to ensure a desired, substantial mixing of the multiphase fluid 22 as it is pumped along the interior of pump housing 24 during operation of pump 20.
  • the ring 38 may be combined with various types of impellers 30 at different positions along the impeller blade tips 46.
  • the impellers 30 may be in the form of helico axial impellers.
  • each impeller blade 42 may be arranged along the impeller hub 40 in a generally helical shape.
  • individual impellers 30 may have more than one wear ring 38 positioned at desired locations along the impeller blade tips 46, e.g. inlet side, outlet side, and/or suitable positions therebetween.
  • a surface 62 of wear ring 38 adjacent surrounding housing 58 may act as a seal surface and may have various configurations.
  • the wear ring surface 62 may be in the form of a plain annular seal, a labyrinth seal, a pocket damper seal, or a stepped diameter segmented seal.
  • wear rings 38 positioned along the blade tips 46 of impeller blades 42 provide impellers 30 with improved rotor dynamic stiffness and dampening. Effectively, the rings 38 work to stabilize an open axial impeller 30 where fluid mixing and viscosity effects may be important factors during pumping operations. However, the reduced axial length 52 of the rings 38 relative to the corresponding impeller blade tip axial length 48 ensures sufficient mixing of multiphase fluid 22 to maintain the multiphase fluid 22 in a desirable condition during pumping. Depending on the parameters of a given operation, the pump 20 may be used in subsea operations or surface operations.
  • the size and configuration of the pump 20 may vary according to the fluid to be pumped and the desired pumping capacity.
  • the arrangement and number of pumping stages 34 also may vary according to the parameters of the desired pumping operations.
  • the number and arrangement of impeller blades 42 as well as the style of impellers 30 also may vary according to the types of fluids 22, e.g. types of multiphase fluids, pumping environment, pump location, and/or other pumping operation parameters.

Landscapes

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

Claims (15)

  1. Système destiné au déplacement de fluide comprenant :
    une pompe axiale multiphase (20) présentant un carter de pompe (24), un arbre (26) monté rotatif dans le carter de pompe (24) et une pluralité de rotors (30) montés sur l'arbre (26), chaque rotor (30) comprenant :
    un moyeu de rotor (40) fixé en rotation sur l'arbre (26) ; et
    une pluralité de pales de rotor (42) s'étendant radialement vers l'extérieur du moyeu de rotor (40), chaque pale de rotor (42) présentant une base de rotor (44) à proximité du moyeu de rotor (40) et dans l'extrémité de rotor (46), les extrémités de rotor (46) présentant une longueur axiale (48) ; caractérisé en ce qu'une bague d'usure (38) est disposée le long des extrémités (46) des pales de rotor (42) et présente une longueur axiale de bague d'usure (52) plus courte que la longueur axiale (48) des extrémités de rotor (46).
  2. Système tel que décrit dans la revendication 1, dans lequel la longueur axiale de la bague d'usure (52) est inférieure à 95 % de la longueur axiale (48) des extrémités de rotor (46).
  3. Système tel que décrit dans la revendication 1, dans lequel la pompe axiale multiphase (20) comprend une pluralité de diffuseurs (32) alternant avec la pluralité de rotors (30).
  4. Système tel que décrit dans la revendication 1, dans lequel la bague d'usure (38) est formée d'un matériau différent de la pluralité de pales de rotor (42).
  5. Système tel que décrit dans la revendication 1, dans lequel la bague d'usure (38) s'étend radialement vers l'extérieur des extrémités de rotor (46).
  6. Système tel que décrit dans la revendication 5, dans lequel la bague d'usure (38) est reçue dans une encoche (56) formée dans une paroi environnante (58).
  7. Système tel que décrit dans la revendication 1, dans lequel la bague d'usure (38) comporte une surface de joint d'étanchéité (62) présentant au moins une forme parmi une forme de joint annulaire, une forme de joint labyrinthe, une forme de joint d'amortissement à poche et une forme de joint segmenté à diamètre étagé.
  8. Système tel que décrit dans la revendication 1, dans lequel la bague d'usure (38) est alignée avec les extrémités de rotor (46).
  9. Système tel que décrit dans la revendication 3, dans lequel la pluralité de rotors (30) est disposée entre les diffuseurs correspondants (32) pour établir les étages de pompe (34).
  10. Système tel que décrit dans la revendication 9, dans lequel les rotors (30) sont des rotors hélicoïdaux axiaux.
  11. Procédé de fabrication d'un système selon la revendication 1, comprenant :
    la fourniture d'une pompe axiale multiphase (20) comportant un rotor (30) présentant une pluralité de pales de rotor (42) dotées d'extrémités de pale (46) s'étendant sur une longueur axiale (48) ;
    le positionnement sûr d'une bague d'usure (38) le long des extrémités de pale (46) pour rigidifier le rotor (30) ; et
    la limitation de la longueur axiale de la bague d'usure (52) à une longueur inférieure à la longueur axiale (48) des extrémités de pale (46) pour permettre l'écoulement sur toute l'étendue des extrémités de pale (46) destinées au mélange de phases actif.
  12. Procédé tel que décrit dans la revendication 11, dans lequel la fourniture de la pompe axiale multiphase (20) comportant le rotor (30) comprend la fourniture d'une pluralité de rotors hélicoïdaux axiaux (30).
  13. Procédé tel que décrit dans la revendication 11, dans lequel le positionnement sûr comprend le positionnement de la bague d'usure (38) à un emplacement souhaité entre un côté entrée et un côté sortie du rotor (30).
  14. Procédé tel que décrit dans la revendication 11, comprenant en outre la fourniture de caractéristiques à une surface de contact entre la bague (38) et les pales de rotor (42) afin de faciliter l'écoulement et le mélange de fluides.
  15. Procédé tel que décrit dans la revendication 11, comprenant en outre la fourniture de la bague (38) comportant une surface de joint d'étanchéité (62) présentant au moins une forme parmi une forme de joint annulaire, une forme de joint labyrinthe, une forme de joint d'amortissement à poche et une forme de joint segmenté à diamètre étagé.
EP19160495.8A 2018-03-07 2019-03-04 Système et méthodologie pour faciliter le pompage de fluide Active EP3536975B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US15/914,253 US20190277302A1 (en) 2018-03-07 2018-03-07 System and methodology to facilitate pumping of fluid

Publications (2)

Publication Number Publication Date
EP3536975A1 EP3536975A1 (fr) 2019-09-11
EP3536975B1 true EP3536975B1 (fr) 2021-04-28

Family

ID=65685235

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19160495.8A Active EP3536975B1 (fr) 2018-03-07 2019-03-04 Système et méthodologie pour faciliter le pompage de fluide

Country Status (2)

Country Link
US (1) US20190277302A1 (fr)
EP (1) EP3536975B1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3739215A1 (fr) * 2020-04-20 2020-11-18 Sulzer Management AG Pompe lubrifiée dans un fluide de traitement
EP3913226A1 (fr) * 2020-05-18 2021-11-24 Sulzer Management AG Pompe à phases multiples

Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2851289A (en) 1957-03-22 1958-09-09 Thiokol Chemical Corp Recirculation seal with plastic wear ring for hydraulic apparatus
US4865519A (en) * 1988-02-12 1989-09-12 Institut Of Engineering Thermophysics Of Chinese Academy Of Sciences Oil submersible pump
FR2697870A1 (fr) 1992-11-09 1994-05-13 Technicatome Pompe axiale à faible débit.
US20020187037A1 (en) 2001-06-08 2002-12-12 Lee Woon Y. Technique for producing a high gas-to-liquid ratio fluid
CN1975172A (zh) 2005-11-28 2007-06-06 宜兴市宙斯泵业有限公司 组合式耐磨叶轮
EP2386767A2 (fr) 2010-05-11 2011-11-16 Sulzer Pumpen AG Pompe hélico-axiale, rotor pour une pompe hélico-axiale, palier hydrodynamique d'un rotor d'une pompe hélico-axiale et pompe hybride dotée d'un rotor pour une pompe hélico-axiale
EP2386766A2 (fr) 2010-05-11 2011-11-16 Sulzer Pumpen AG Pompe hélico-axiale, rotor pour une pompe hélico-axiale, palier hydrodynamique d'un rotor d'une pompe hélico-axiale et pompe hybride dotée d'un rotor pour une pompe hélico-axiale
US8075272B2 (en) 2008-10-14 2011-12-13 General Electric Company Steam turbine rotating blade for a low pressure section of a steam turbine engine
US20130094944A1 (en) 2011-10-12 2013-04-18 General Electric Company Bucket assembly for turbine system
US20150354373A1 (en) 2014-06-04 2015-12-10 United Technologies Corporation Cutting blade tips
US20160222977A1 (en) * 2013-09-11 2016-08-04 IFP Energies Nouvelles Multiphase pump impeller with means of amplifying and distributing clearance flows
DE102015210601A1 (de) 2015-06-10 2016-12-15 Voith Patent Gmbh Laufrad für eine Pumpe oder Turbine

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1481552A (en) * 1922-07-14 1924-01-22 Standard Deep Well Pump Co Inc Pump
US2440947A (en) * 1945-01-11 1948-05-04 Smith Corp A O Centrifugal pump with impeller supporting wear rings
FR2670539B1 (fr) * 1990-12-14 1994-09-02 Technicatome Pompe multi-etagee destinee particulierement au pompage d'un fluide multiphasique.
US5476363A (en) * 1993-10-15 1995-12-19 Charles E. Sohl Method and apparatus for reducing stress on the tips of turbine or compressor blades

Patent Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2851289A (en) 1957-03-22 1958-09-09 Thiokol Chemical Corp Recirculation seal with plastic wear ring for hydraulic apparatus
US4865519A (en) * 1988-02-12 1989-09-12 Institut Of Engineering Thermophysics Of Chinese Academy Of Sciences Oil submersible pump
FR2697870A1 (fr) 1992-11-09 1994-05-13 Technicatome Pompe axiale à faible débit.
US20020187037A1 (en) 2001-06-08 2002-12-12 Lee Woon Y. Technique for producing a high gas-to-liquid ratio fluid
CN1975172A (zh) 2005-11-28 2007-06-06 宜兴市宙斯泵业有限公司 组合式耐磨叶轮
US8075272B2 (en) 2008-10-14 2011-12-13 General Electric Company Steam turbine rotating blade for a low pressure section of a steam turbine engine
EP2386767A2 (fr) 2010-05-11 2011-11-16 Sulzer Pumpen AG Pompe hélico-axiale, rotor pour une pompe hélico-axiale, palier hydrodynamique d'un rotor d'une pompe hélico-axiale et pompe hybride dotée d'un rotor pour une pompe hélico-axiale
EP2386766A2 (fr) 2010-05-11 2011-11-16 Sulzer Pumpen AG Pompe hélico-axiale, rotor pour une pompe hélico-axiale, palier hydrodynamique d'un rotor d'une pompe hélico-axiale et pompe hybride dotée d'un rotor pour une pompe hélico-axiale
US20130094944A1 (en) 2011-10-12 2013-04-18 General Electric Company Bucket assembly for turbine system
US20160222977A1 (en) * 2013-09-11 2016-08-04 IFP Energies Nouvelles Multiphase pump impeller with means of amplifying and distributing clearance flows
US20150354373A1 (en) 2014-06-04 2015-12-10 United Technologies Corporation Cutting blade tips
DE102015210601A1 (de) 2015-06-10 2016-12-15 Voith Patent Gmbh Laufrad für eine Pumpe oder Turbine

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
TANG JIN, ET AL: "Use of partially shrouded impeller in a small centrifugal compressor", JOURNAL OF THERMAL SCIENCE, vol. 17, no. 1, 1 January 2008 (2008-01-01), pages 21 - 27, XP055889509

Also Published As

Publication number Publication date
EP3536975A1 (fr) 2019-09-11
US20190277302A1 (en) 2019-09-12

Similar Documents

Publication Publication Date Title
EP2841826B1 (fr) Joint à labyrinthe à amortissement élevé comportant un motif hélicoïdal ou hélicoïdal-cylindrique mixte
US9874220B2 (en) Anti-swirl device
US7775763B1 (en) Centrifugal pump with rotor thrust balancing seal
EP2516867B1 (fr) Garniture abradable avec offset axial
EP2151583A2 (fr) Compresseur centrifuge
US20040150164A1 (en) Sealing arrangement
JP2010236555A (ja) 改良されたポンプのインペラ
EP1967774A1 (fr) Ensemble multi-arbres coaxial
EP3536975B1 (fr) Système et méthodologie pour faciliter le pompage de fluide
RU2394173C2 (ru) Рабочее колесо для центробежного насоса и содержащий его центробежный насос
JP2014521016A (ja) 多段遠心ターボ機械
US7273352B2 (en) Inlet partial blades for structural integrity and performance
CN111263846A (zh) 压气机翼型
US20050191172A1 (en) Inducer with shrouded rotor for high speed applications
WO2019163162A1 (fr) Palier lisse à patins oscillants et machine rotative l'utilisant
JP6684842B2 (ja) タービン動翼及び回転機械
JP2017155625A (ja) シール構造及びターボ機械
WO2016157530A1 (fr) Pale de rotor et machine rotative à écoulement axial
JPH0719005A (ja) ラビリンスシール装置
JP2019124277A (ja) ティルティングパッド軸受装置及び回転機械
JP2015137607A (ja) 動翼、及び軸流回転機械
US11781556B2 (en) High energy density turbomachines
JP2006183475A (ja) 遠心圧縮機
JP4556465B2 (ja) インデューサ装置
US20130170993A1 (en) Blade shroud for fluid element

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

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

Free format text: STATUS: THE APPLICATION HAS BEEN PUBLISHED

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL 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 RS SE SI SK SM TR

AX Request for extension of the european patent

Extension state: BA ME

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

Free format text: STATUS: REQUEST FOR EXAMINATION WAS MADE

17P Request for examination filed

Effective date: 20200311

RBV Designated contracting states (corrected)

Designated state(s): AL 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 RS SE SI SK SM TR

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

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

Free format text: STATUS: GRANT OF PATENT IS INTENDED

INTG Intention to grant announced

Effective date: 20201202

RIN1 Information on inventor provided before grant (corrected)

Inventor name: KLEPSVIK, KNUT HARALD

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

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

Free format text: STATUS: THE PATENT HAS BEEN GRANTED

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AL 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 RS SE SI SK SM TR

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: AT

Ref legal event code: REF

Ref document number: 1387374

Country of ref document: AT

Kind code of ref document: T

Effective date: 20210515

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 602019004123

Country of ref document: DE

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG9D

REG Reference to a national code

Ref country code: NO

Ref legal event code: T2

Effective date: 20210428

REG Reference to a national code

Ref country code: AT

Ref legal event code: MK05

Ref document number: 1387374

Country of ref document: AT

Kind code of ref document: T

Effective date: 20210428

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210428

Ref country code: HR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210428

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210428

Ref country code: NL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210428

Ref country code: AT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210428

Ref country code: BG

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210728

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210729

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210828

Ref country code: SE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210428

Ref country code: RS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210428

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210830

Ref country code: LV

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210428

Ref country code: PL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210428

REG Reference to a national code

Ref country code: NL

Ref legal event code: MP

Effective date: 20210428

REG Reference to a national code

Ref country code: DE

Ref legal event code: R026

Ref document number: 602019004123

Country of ref document: DE

PLBI Opposition filed

Free format text: ORIGINAL CODE: 0009260

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: RO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210428

Ref country code: SM

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210428

Ref country code: CZ

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210428

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210428

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210428

Ref country code: EE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210428

Ref country code: ES

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210428

PLAX Notice of opposition and request to file observation + time limit sent

Free format text: ORIGINAL CODE: EPIDOSNOBS2

26 Opposition filed

Opponent name: SULZER MANAGEMENT AG

Effective date: 20220126

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210828

Ref country code: AL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210428

PLBB Reply of patent proprietor to notice(s) of opposition received

Free format text: ORIGINAL CODE: EPIDOSNOBS3

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210428

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 602019004123

Country of ref document: DE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MC

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210428

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

REG Reference to a national code

Ref country code: BE

Ref legal event code: MM

Effective date: 20220331

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20220304

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20220331

Ref country code: IE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20220304

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20220331

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20221001

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20220331

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20220331

PLCK Communication despatched that opposition was rejected

Free format text: ORIGINAL CODE: EPIDOSNREJ1

APAH Appeal reference modified

Free format text: ORIGINAL CODE: EPIDOSCREFNO

APBM Appeal reference recorded

Free format text: ORIGINAL CODE: EPIDOSNREFNO

APBP Date of receipt of notice of appeal recorded

Free format text: ORIGINAL CODE: EPIDOSNNOA2O

APBQ Date of receipt of statement of grounds of appeal recorded

Free format text: ORIGINAL CODE: EPIDOSNNOA3O

P01 Opt-out of the competence of the unified patent court (upc) registered

Effective date: 20231212

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210428

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210428

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20240108

Year of fee payment: 6

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: HU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT; INVALID AB INITIO

Effective date: 20190304

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: NO

Payment date: 20240222

Year of fee payment: 6