EP4390134A1 - Pompe submersible à plusieurs étages - Google Patents

Pompe submersible à plusieurs étages Download PDF

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Publication number
EP4390134A1
EP4390134A1 EP22214787.8A EP22214787A EP4390134A1 EP 4390134 A1 EP4390134 A1 EP 4390134A1 EP 22214787 A EP22214787 A EP 22214787A EP 4390134 A1 EP4390134 A1 EP 4390134A1
Authority
EP
European Patent Office
Prior art keywords
impeller
pressure stage
diffuser
submergible
multistage 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.)
Pending
Application number
EP22214787.8A
Other languages
German (de)
English (en)
Inventor
Jan WIKSTRÖM
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.)
Xylem Europe GmbH
Original Assignee
Xylem Europe GmbH
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
Application filed by Xylem Europe GmbH filed Critical Xylem Europe GmbH
Priority to EP22214787.8A priority Critical patent/EP4390134A1/fr
Priority to PCT/EP2023/085056 priority patent/WO2024132624A1/fr
Publication of EP4390134A1 publication Critical patent/EP4390134A1/fr
Pending legal-status Critical Current

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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
    • F04D13/00—Pumping installations or systems
    • F04D13/02—Units comprising pumps and their driving means
    • F04D13/06—Units comprising pumps and their driving means the pump being electrically driven
    • F04D13/08—Units comprising pumps and their driving means the pump being electrically driven for submerged use
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D1/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D1/06—Multi-stage pumps
    • F04D1/063—Multi-stage pumps of the vertically split casing type
    • 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
    • F04D29/167—Sealings between pressure and suction sides especially adapted for liquid pumps of a centrifugal 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
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/44—Fluid-guiding means, e.g. diffusers
    • F04D29/445—Fluid-guiding means, e.g. diffusers especially adapted for liquid pumps

Definitions

  • the present invention relates generally to the field of pumps configured to pump liquid comprising solid/abrasive matter. Further, the present invention relates specifically to the field of submergible pumps such as dewatering pumps and drainage pumps especially configured for pumping liquid comprising solid matter, such as sand and stone material.
  • the pumped liquid is for instance drilling water in mining/tunneling applications, surface water on construction sites, etc. i.e. transport and dewatering applications.
  • the present invention relates specifically to a submergible multistage pump suitable for said applications, wherein the pump comprises a plurality of pressure stages connected in series.
  • the inventive pump may be entirely wet installed or partly dry installed, and is of submergible type in both installations.
  • the present invention relates to a submergible multistage pump comprising a drive unit having an electric motor and a drive shaft, wherein the drive shaft extends in the axial direction, and a hydraulic unit connected to the drive unit and comprising a leading pressure stage, a trailing pressure stage and a top element connected in series, wherein the top element comprises an outlet of the multistage pump.
  • the leading pressure stage of the hydraulic unit comprises an axial inlet, an axial outlet, a circumferential housing, a circumferential internal diffuser, and an impeller connected to the drive shaft of the drive unit, wherein the housing, the diffuser and the impeller of the leading pressure stage define a flow path from the axial inlet to the axial outlet, and wherein the diffuser is connected to the housing.
  • the location of the impeller side of the gap i.e. the location of the impellers
  • the location of the stationary side of the gap i.e. the location of the diffusers
  • the housing of the hydraulic unit that is connected to the housing of the drive unit.
  • a known way to try to provide small gaps is to have a lining of resilient material at the stationary parts, whereby some contact is allowed between the rotating part and the stationary part without entailing wear and risk for damages to the components.
  • the lining is not as resistive to wear as metal, and the abrasive matter will inevitably provide wear to the lining.
  • the site manager i.e. the process at the working site, requires a constant low liquid level and therefor the drainage pump is in constant operation even though there is only little water/liquid available in the cavity/basins.
  • the water can be constituted by ground water leakage, rain water, and especially process water from drilling, reducing dust, etc. If the water is not removed the production will be negatively affected, which cannot be accepted.
  • the water is pumped/transported by means of dewatering/drainage pumps.
  • the drainage pumps are in constant operation, irrespective of water being pumped or not. If the stationary parts and the rotating impeller comes in contact with each other at the gap when no media is pumped or present in the gap, the components are more susceptible for damage/wear. Due to the long tolerance chains and the risk of damage, the gaps of the prior art pumps are wider then optimal considered from a back flow point of view.
  • a primary object of the present invention is to provide an improved multistage pump of the initially defined type that comprises a construction that makes it possible to have small gaps between the stationary parts and the rotating impellers of the multistage pump without needing to conduct labor-intensive and expensive manufacturing/machining of the components of the multistage pump.
  • the leading pressure stage comprises radial play between the housing and the diffuser in the radial direction, and abutment between the housing and the diffuser in the axial direction.
  • the present invention is based on the insight that by not having the diffuser fixedly connected/bolted to the housing of the hydraulic unit but floating in the radial direction during mounting thanks to the radial play in the radial direction, the location of the diffuser is instead determined directly by the location of the impeller, i.e. the location of the stationary side of the gap is directly dependent on the location of the impeller side of the gap.
  • the gap may be checked/secured using a thickness gauge, tape, etc. The tolerance chain is made minimal resulting in a possibility to have a small gap without needing to conduct labor-intensive and expensive manufacturing/machining, and thereby less back flow and less wear thereby longer service interval may be applied.
  • the hydraulic unit comprises at least one intermediate pressure stage arranged between and connected in series with the leading pressure stage and the trailing pressure stage, wherein the at least one intermediate pressure stage is configured as the leading pressure stage.
  • each diffuser comprises an upper diffuser element and a lower diffuser element, said upper diffuser element and said lower diffuser element being connected to each other and jointly displaceable in the radial direction in relation to the housing during assembly of the pump.
  • the lower diffuser element is configured to direct the pumped media from the impeller outwards towards the housing
  • the upper diffuser element is configured to direct the pumped media from the housing inwards towards the axial outlet of the pressure stage, i.e. towards the axial inlet of the subsequent pressure stage or of the top element.
  • each pressure stage comprises an upper face seal at the interface between the impeller and the diffuser adjacent the axial outlet of the pressure stage.
  • each pressure stage comprises a lower face seal at the interface between the impeller and the diffuser adjacent the axial inlet of the pressure stage.
  • the radial gap width of the upper face seal is equal to or less than the radial gap width of the lower face seal.
  • the present invention relates specifically to the field of submergible pumps especially configured for pumping liquid comprising abrasive/solid matter, such as water comprising sand and stone material.
  • the submergible pumps are especially drainage/dewatering pumps.
  • the present invention relates specifically to a submergible multistage pump configured for drainage/dewatering applications.
  • FIG. 1 discloses a schematic perspective view from above of the pump 1 and figure 2 disclose a schematic illustration of a cross-sectional side view of parts of the pump 1 according to figure 1 .
  • the general structural elements of a pump 1 will be described with reference to figures 1 and 2 , wherein the pump 1 comprises two major parts, i.e. a drive unit, generally designated 2, and a hydraulic unit, generally designated 3.
  • the hydraulic unit 3 of the pump 1 comprises an inlet 4, an outlet 5 and a pump chamber 6 located intermediate said inlet 4 and said outlet 5, i.e. the pump chamber 6 is located downstream the inlet 4 and upstream the outlet 5.
  • the inlet 4 is an axial inlet and the outlet 5 is a radial outlet.
  • the outlet 5 of the hydraulic unit 3 also constitutes the outlet of the pump 1 (as disclosed in figures 1 and 2 ) and in other applications the outlet 5 of the hydraulic unit 3 is connected to a separate outlet of the pump 1, e.g. via a cooling jacket volume.
  • the outlet of the pump 1 is configured to be connected to an outlet conduit (not shown).
  • Figure 2 disclose a hydraulic unit 3 of a multistage pump 1 and portions of the drive unit 2.
  • the drive unit 2 is located separated from the hydraulic unit 3 by an inlet volume 7.
  • the inlet volume 7 is delimited by an inlet strainer 8.
  • the drive unit 2 is located on the upstream side of the inlet 4 (and the inlet volume 7) of the hydraulic unit 3.
  • the inlet strainer 8 comprises perforations or holes, wherein the inlet strainer 8 is configured to prevent larger objects from reaching the inlet 4 of the hydraulic unit 3.
  • the pump 1 the drive unit 2 is located on the downstream side of the inlet 4 of the hydraulic unit 3, wherein the pump 1 comprises an intermediate wall structure separating the hydraulic unit 3 from the drive unit 2 in a liquid tight manner.
  • the intermediate wall structure may comprise a liquid seal chamber or the like sealing arrangement between the pump chamber 6 of the hydraulic unit 3 and a motor compartment 9 of the drive unit 2.
  • Such pumps 1 still comprise an inlet strainer 8 and an inlet volume 7.
  • the drive unit 2 of the pump 1 comprises an electric motor, generally designated 10, arranged in the motor compartment 9 delimited by a liquid tight pump housing 11,
  • the drive unit 2 also comprises a drive shaft 12 extending from the electric motor 10 to the pump chamber 6.
  • the drive shaft 12 extends from the drive unit 2 through the inlet volume 7 to the hydraulic unit 3.
  • the electric motor 10 comprises a stator 13 and a rotor 14, wherein the drive shaft 12 is connected to the rotor 14 of the electric motor 10 in conventional way.
  • the pump 1, more precisely the electric motor 10, is operatively connected to a control unit 15, such as an Intelligent Drive comprising a Variable Frequency Drive (VFD).
  • VFD Variable Frequency Drive
  • said pump 1 is configured to be operated at a variable operational speed [rpm], by means of said control unit 15.
  • the control unit is located inside the liquid tight pump housing 11, e.g. in an electronics chamber 16 of the drive unit 2, i.e. it is preferred that the control unit 15 is integrated into the pump 1.
  • the electronics/connection chamber 16, is separated from the motor compartment 9 in a liquid tight manner.
  • the control unit 15 is configured to control the operational speed of the pump 1.
  • the control unit is an external control unit, or the control unit is divided into an external sub-unit and an internal sub-unit.
  • the operational speed of the pump 1 is more precisely the rpm of the electric motor 10 and correspond/relate to a control unit output frequency.
  • the control unit 15 is configured and capable of operating the pump 1 in a normal direction of rotation, i.e. forward, in order to pump liquid, and in an opposite direction of rotation, i.e. backwards, in order to clean or unblock the pump chamber 6.
  • the electric motor 10 is powered via at least one electric power cable 17 extending from a power supply, and the pump 1 comprises a liquid tight lead-through 18 receiving each electric power cable 17.
  • the components of the pump 1 are usually cold down by means of the liquid/water surrounding the pump 1, i.e. when the pump 1 is in a submerged configuration/application.
  • the pump 1 comprises dedicated cooling systems.
  • Both configurations comprise a submergible pump 1, i.e. the pump 1 is designed and configured to be able to operate in a submerged configuration/position, i.e. during operation be located entirely under the liquid surface.
  • the submersible pump 1 during operation must not be entirely located under the liquid surface but may continuously or occasionally be fully or partly located above the liquid surface.
  • Each pressure stage comprises an impeller 20 connected to the drive shaft 12, wherein the impeller 20 is driven in rotation during operation of the pump 1 whereby liquid is sucked into the inlet 4 and pumped out through the outlet 5 by means of the rotating impeller 20 when the pump 1 is active.
  • the impeller 20 is a channel impeller having so-called closed channels.
  • the impeller 20 is concentric to the drive shaft 12.
  • Each pressure stage also comprises a circumferential housing 21 and a circumferential internal diffuser 22, wherein the housing 21, the diffuser 22 and the impeller 20 define a flow path from the inlet to the outlet of the pressure stage.
  • the diffuser 22 is connected to the housing 21, wherein the diffuser 22 and the housing 21 are stationary.
  • the pump housing 11, the housing 21, the diffuser 22, the impeller 20, and other essential components, are preferably made of metal, such as aluminum and steel.
  • the present invention is based on a new and improved multistage pump 1, that is configured to be used for pumping abrasive media, for instance water comprising sand and stones.
  • the impeller 20 comprises a hub 23, an upper cover disc/plate 24 connected to the centrally located hub 23, a lower cover disc/plate 25 and at least one vane 26 extending between and connecting the upper cover disc 24 and the lower cover disc 25.
  • the impeller 20 preferably comprises a plurality of vanes/blades 26 that are equidistantly located around the hub 23.
  • the vane/vanes 26 are preferably spirally swept from an inner leading edge to an outer trailing edge, i.e. in the direction from the hub 23 towards the periphery of the impeller 20, in a direction opposite the direction of rotation of the impeller 20 during normal (liquid pumping) operation of the pump 1.
  • Each blade 26 comprises a leading edge 27 adjacent the hub 23 and a trailing edge 28 at the periphery of the impeller 20, wherein two adjacent blades 26 together defines a channel extending from the leading edges 27 to the trailing edges 28.
  • the leading edges 27 grabs hold of the liquid
  • the channels accelerate the liquid and the liquid leaves the impeller 20 at the trailing edges 28.
  • the liquid is guided by the diffusers 22 and housing 21 towards the outlet.
  • Said channels are also delimited by the upper cover plate 24 and the lower cover plate 25 of the impeller 20.
  • the diameter of the impeller 20 and the shape and configuration of the channels/vanes determines the pressure build up in the liquid and the pumped flow.
  • the hydraulic unit 3 of the inventive multistage pump 1 comprises a leading pressure stage and a trailing pressure stage, wherein the leading pressure stage is the most upstream pressure stage and wherein the trailing pressure stage is the most downstream pressure stage, seen in the flow direction.
  • the leading pressure stage of the hydraulic unit 3 comprises an axial inlet 29 and an axial outlet 30.
  • the inlet 29 and the outlet 30 are located around the drive shaft 12 in a concentric manner.
  • the inlet 29 of the leading pressure stage is also the inlet 4 of the hydraulic unit 3.
  • the leading pressure stage comprises radial play between the housing 21 and the diffuser 22 in the radial direction, and abutment between the housing 21 and the diffuser 22 in the axial direction.
  • the diffuser 22 is displaceable in the radial direction during mounting/assembly in relation to the housing 21 by having the location of the diffuser 22 adjusted to the location of the impeller 20 by controlling the interface between the impeller 20 and the diffuser 22 adjacent the axial outlet 30 of the leading pressure stage.
  • This adjustment can be made with a tape, a thickness gauge, etc.
  • the top unit 19 is clamped to the housing 21 of the leading pressure stage, using a set of bolts 31, the diffuser 22 is clamped in the axial direction and thereby fixated also in the radial direction.
  • the radial play between the diffuser 22 and the housing 21, i.e. non abutment in the radial direction, is present also when the hydraulic unit 3 is clamped.
  • the diffuser 22 is concentric to the drive shaft 12 even though the housing 21 might have a small axial misalignment with the drive shaft 12. Thanks to the invention the radial width of the gap between the impeller 20 and the diffuser 22 at the interface adjacent the axial outlet 30 of the leading pressure stage can be made much smaller/tighter than previous solutions.
  • the upper face seal has an axially extending gap between an outer diameter of the upper seal member 32 of the impeller 20 and an inner diameter of the upper seal member 33 of the diffuser 22.
  • the upper seal member 32 of the impeller 20 is located in a circumferential upper seat 34 having an envelope surface.
  • the upper seal member 33 of the diffuser 22 is preferably in press fit engagement with the diffuser 22, in order to avoid use of glue/adhesive.
  • the upper seal member/ring 33 of the diffuser 22 is subject to compressive force/strain.
  • the upper seal member 32 of the impeller 20 and the upper seal member 33 of the diffuser 22 are made of material that is less affected by wear than the impeller 20 and the diffuser 22.
  • the upper seal member 32 of the impeller 20 and the upper seal member 33 of the diffuser 22 preferably comprises or is made of cemented carbide or the like.
  • the inventor has identified that the upper seal member 32 of the impeller 20 shall not be exposed to elevated tensile force, due to the risk of breaking/bursting, and thereby must not be in press fit engagement with the upper seat 34 of the impeller 20.
  • the inner diameter of the upper seal member 32 is larger than the diameter of the envelope surface of the upper seat 34.
  • the impeller 20 comprises a resilient member 35 that is located between and separates the upper seal member 32 and the upper seat 34 in the radial direction.
  • the resilient member 35 between the upper seal member 32 and the upper seat 34 is preferably constituted by a rubber O-ring.
  • the resilient member 34 works as a damper, i.e. entailing that the upper seal member 32 may be slightly displaced in the radial direction should it be exposed to external force in the radial direction, i.e. due to contact between the upper seal member 32 of the impeller 20 and the upper seal member 33 of the diffusor 22.
  • the impeller 20 of all pressure stages comprises a lower face seal at the interface between the impeller 20 and the diffuser 22 adjacent the axial inlet of the pressure stage.
  • Such lower face seal comprises a lower seal member 36 connected to the lower cover disc 25, and a lower seal member 37 connected to the diffuser 22.
  • the lower seal member 36 of the impeller 20 co-rotates with the impeller and the lower seal member 37 of the diffuser 22 is stationary.
  • the lower face seal has an axially extending gap between an outer diameter of the lower seal member 36 of the impeller 20 and an inner diameter of the lower seal member 37 of the diffuser 22.
  • the lower seal member 36 of the impeller 20 is located in a circumferential lower seat 38 having an envelope surface.
  • the lower seal member 37 of the diffuser 22 is preferably in press fit engagement with the diffuser 22, in order to avoid use of glue/adhesive.
  • the lower seal member/ring 37 of the diffuser 22 is subject to compressive force/strain.
  • the lower seal member 34 of the impeller 20 and the lower seal member 37 of the diffuser 22 are made of material that is less affected by wear than the impeller 20 and the diffuser 22.
  • the lower seal member 34 of the impeller 20 and the lower seal member 37 of the diffuser 22 preferably comprises or is made of cemented carbide or the like.
  • the impeller 20 comprises a retainer ring 39 that is in press fit connection with the envelope surface of the lower seat 38 of the impeller 20, wherein the retainer ring 39 is configured to retain/clamp the lower seal member 36 in the lower seat 38 of the lower cover disc 25.
  • the retainer ring 39 is made of material that is able to withstand greater tensile forces than the lower seal member 36.
  • the retainer ring 39 is preferably made of duplex stainless steel or the like.
  • the envelope surface of the lower seat 38 of the lower cover disc 25 may have different diameters for the lower seal member 36 and the retainer ring 39.
  • the outer diameter of the retainer ring 39 is smaller than the outer diameter of the lower seal member 36. Therefore, it is easier to mount/insert the impeller 20 into the lower seal member 37 of the diffuser 22, thanks to the smaller outer diameter of the retainer ring 39.
  • a resilient member 40 is located between and separates the lower seal member 36 and the lower seat 38 in the radial direction.
  • the resilient member 40 is preferably constituted by a rubber O-ring.
  • the retainer ring 39 abuts the resilient member 40, and the lower seal member 36.
  • the retainer ring 39 clamps the lower seal member 36 in the axial direction in order to have the lower seal member 36 co-rotate with the impeller 20.
  • the resilient member 40 also promotes co-rotation of the lower seal member 36 and the impeller 20.
  • the resilient member 40 works as a damper, i.e.
  • the lower seal member 36 may be slightly displaced in the radial direction should it be exposed to external force in the radial direction, i.e. due to contact between the lower seal member 36 of the impeller 20 and the lower seal member 37 of the diffusor 22.
  • the outer diameter of the lower seal member 36 of the impeller 20 is greater than the outer diameter of the upper seal member 32 of the impeller 20.
  • the radial gap width of the upper face seal is equal to or less than the radial gap width of the lower face seal, thereby in case of drive shaft 12 deflection the upper face seal will contact before the lower face seal which is preferred since the mutual surface velocity is lower at the upper face seal than at the lower face seal.
  • the radial gap width of the upper face seal is equal to or more than 0,05 mm and equal to or less than 0,25 mm, preferably 0,15 mm
  • the radial gap width of the lower face seal is equal to or more than 0,1 mm and equal to or less than 0,3 mm, preferably 0,2 mm.
  • the trailing pressure stage of the hydraulic unit 3 is configured as the leading pressure stage, i.e. comprises the same type of lower face seal and the same type of upper face seal and having an axial inlet and an axial outlet. As disclosed in the various figures.
  • the trailing pressure stage does not comprise the upper face seal but instead the diffuser 22 of the trailing pressure stage comprises a stationary cap covering the upper end of the drive shaft 12 and impeller 20, wherein the stationary cap is connected to the diffuser 22 when the location of the diffuser 22 is fixed by clamping the top unit 19 to the housing 21 of the leading pressure stage.
  • the stationary cap may also be used when the trailing pressure stage comprises an upper face seal.
  • One advantage of having such a stationary cap is that the elevated return pressure from the liquid in the outlet conduit does not act against the drive shaft 12 and thereby the bearing arrangement of the drive shaft 12 is under less stress.
  • the trailing pressure stage together with the top element 19 comprise a radial outlet.
  • the hydraulic unit 3 comprises at least one intermediate pressure stage arranged between and connected in series with the leading pressure stage and the trailing pressure stage, wherein the at least one intermediate pressure stage is configured as the leading pressure stage, i.e. comprises the same type of lower face seal and the same type of upper face seal and having an axial inlet and an axial outlet. As disclosed in figure 2 .
  • the drive shaft 12 is journalled in the drive unit 2 and comprises a free end connected to the impeller 20 of the trailing pressure stage.
  • the hydraulic unit 3 comprises four or more pressure stages the drive shaft 12 is journalled also at the upper end in the hydraulic unit 3.
  • each diffuser 22 comprises an upper diffuser element 41 and a lower diffuser element 42, said upper diffuser element 41 and said lower diffuser element 42 being connected to each other and jointly displaceable in the radial direction in relation to the housing 21 during assembly/mounting of the pump 1.
  • the location of the lower diffuser element 42 in the radial direction in relation to the housing 21 is determined by the location of the upper diffuser element 41 in the radial direction in relation to the impeller 20 and drive shaft 12.
  • the diffuser 22 is concentric to the drive shaft 12.
  • the lower diffuser element 42 comprises at least one circumferential ridge 43 on the side facing the lower cover disc 25 of the impeller 20, wherein the radial distance between said ridge 43 and the lower seal member 37 of the diffuser 22 is equal to or more than 1/3 and equal to or less than 2/3 of the radial distance between the outer edge of the lower cover disc 25 of the impeller 20 and the lower seal member 37 of the diffuser 22.
  • the circumferential ridge 43 has the purpose to prevent solid matter from reaching the lower face seal.
  • the abrasive matter will follow the surface flow closest to the lower cover disc 25 of the impeller 20 outwards.
  • the abrasive matter is halted at a distance less than 1/3 of the radial distance between the outer edge of the lower cover disc 25 of the impeller 20 and the lower seal member 37 of the diffuser 22
  • the surface flow is too weak to bring the abrasive matter outwards and the abrasive matter will start grinding holes in the lower diffuser element 42.
  • the abrasive matter passes the location of the 1/3 of the distance, it is better to let the abrasive matter reach the lower face seal and be grinded therein and removed through the axial gap.
  • the hub 23 of the impeller 20 of one pressure stage abuts the hub 23 of the impeller 20 of the adjacent pressure stage. Since all gaps between the impeller 20 and the diffuser 22 are axial, there is no need to have axial trimming of the location of each impeller 20 but the overall configuration/design admit some axial displacement between the drive shaft 12 and impellers 20 in relation to the top element 19 and diffusers 22. Thus, there is axial play between the impeller 20 and the diffuser 22. Thereto the hub 23 of the downstream impeller 20 also retain the upper seal member 32 of the upstream impeller 20 in the upper seat 34.
  • the housing 21 of the leading pressure stage is connected to the housing 11 of the drive unit 2 such that the housing 21 is as concentric as possible to the drive shaft 12. Then the upper end of the drive shaft 12 is located well above the leading pressure stage. Thereafter the lower diffuser element 42 is inserted into the housing 21 and abuts a seat in the axial direction. The lower diffuser element 42 and/or the housing 21 may comprise means to prevent mutual rotation. Thereafter the impeller 20 is slipped on to the drive shaft 12 and the retainer ring 39 and the lower seal member 36 are inserted into the lower seal member 37. The impeller 20 abuts a radially extending collar 44 or the like on the drive shaft 12.
  • the upper diffuser element 41 is lowered over the impeller 20 until the upper seal member 33 of the diffuser 22 is located around the upper seal member 32 of the impeller 20. At the same time the upper diffuser element 41 engage the lower diffuser element 42.
  • the lower diffuser element 42 and/or the upper diffuser element 41 may comprise means to prevent mutual rotation.
  • the lower diffuser element 42 and the upper diffuser element 41 comprise means to prevent mutual displacement in the radial direction.
  • the radial gap width of the upper face seal is adjusted by means of thickness gauge, tape, etc. in order to have concentricity between the drive shaft 12 and the diffuser 22.
  • the drive shaft 12 and impeller 20 is preferably rotated to ensure that there is non-contact between the impeller 20 and diffuser 22. Since the upper diffuser element 41 and the lower diffuser element 42 act as one element, the lower face seal is adjusted at the same time as the upper face seal is adjusted even though the lower face seal is not visible for the operator.
  • the housing 21 of the downstream pressure stage is connected to the housing 21 of the upstream pressure stage, i.e. fixated/guided in the radial direction, and at the same time the housing of the downstream pressure stage abuts the upper diffuser element 41 of the upstream pressure stage. There is still a small gap in the axial direction between the housing 21 of the downstream pressure stage and the housing 21 of the upstream pressure stage. Thereafter the lower diffuser element 42, the impeller 20 and the upper diffuser element 41 are added in the same way as disclosed above.
  • the lower diffuser element 42 of the downstream pressure stage abuts the upper diffuser element 41 of the upstream pressure stage.
  • the hub 23 of the downstream impeller 20 abuts the hub 23 of the upstream impeller 20.
  • the housing 21 of the downstream pressure stage and/or the housing 21 of the upstream pressure stage may comprise means to prevent mutual rotation.
  • the radial gap width of the upper face seal of each pressure stage is adjusted by means of thickness gauge, tape, etc. in order to have concentricity between the drive shaft 12 and the diffuser 22.
  • top element 19 is connected to the housing 21 of the trailing pressure stage, i.e. fixated/guided in the radial direction, and at the same time the top element 19 abuts the upper diffuser element 41 of the trailing pressure stage. There is still a small gap in the axial direction between the top element 19 and the housing 21 of the trailing pressure stage.
  • An end member 45 is connected to the free upper end of the drive shaft 12 to secure the impellers 20 to the drive shaft 20.
  • the end member 45 may be added before or after the top element 19.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
EP22214787.8A 2022-12-20 2022-12-20 Pompe submersible à plusieurs étages Pending EP4390134A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP22214787.8A EP4390134A1 (fr) 2022-12-20 2022-12-20 Pompe submersible à plusieurs étages
PCT/EP2023/085056 WO2024132624A1 (fr) 2022-12-20 2023-12-11 Pompe submersible à étages multiples

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP22214787.8A EP4390134A1 (fr) 2022-12-20 2022-12-20 Pompe submersible à plusieurs étages

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EP4390134A1 true EP4390134A1 (fr) 2024-06-26

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EP22214787.8A Pending EP4390134A1 (fr) 2022-12-20 2022-12-20 Pompe submersible à plusieurs étages

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EP (1) EP4390134A1 (fr)
WO (1) WO2024132624A1 (fr)

Citations (5)

* Cited by examiner, † Cited by third party
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GB1110660A (en) * 1966-05-20 1968-04-24 Sumo Pumps Ltd Improvements relating to sealing means for centrifugal pumps
US3612716A (en) * 1970-06-15 1971-10-12 Red Jacket Mfg Co Multistage centrifugal pump
US20060269404A1 (en) * 2005-05-26 2006-11-30 Franklin Electric Co., Inc. Multistage pump
CN203717362U (zh) * 2014-02-13 2014-07-16 山东长志泵业有限公司 高速加氢进料泵
EP3798449A1 (fr) * 2019-09-24 2021-03-31 Sulzer Management AG Pompe pour transporter un fluide

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US3730641A (en) * 1972-03-10 1973-05-01 Flint & Walling Inc Centrifugal pumps

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1110660A (en) * 1966-05-20 1968-04-24 Sumo Pumps Ltd Improvements relating to sealing means for centrifugal pumps
US3612716A (en) * 1970-06-15 1971-10-12 Red Jacket Mfg Co Multistage centrifugal pump
US20060269404A1 (en) * 2005-05-26 2006-11-30 Franklin Electric Co., Inc. Multistage pump
CN203717362U (zh) * 2014-02-13 2014-07-16 山东长志泵业有限公司 高速加氢进料泵
EP3798449A1 (fr) * 2019-09-24 2021-03-31 Sulzer Management AG Pompe pour transporter un fluide

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