EP4343152A1 - Pompe à turbine verticale - Google Patents

Pompe à turbine verticale Download PDF

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Publication number
EP4343152A1
EP4343152A1 EP23193820.0A EP23193820A EP4343152A1 EP 4343152 A1 EP4343152 A1 EP 4343152A1 EP 23193820 A EP23193820 A EP 23193820A EP 4343152 A1 EP4343152 A1 EP 4343152A1
Authority
EP
European Patent Office
Prior art keywords
manifold
riser pipe
turbine pump
vertical turbine
manifold end
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
EP23193820.0A
Other languages
German (de)
English (en)
Inventor
Alexander Bichner
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.)
Wilo SE
Original Assignee
Wilo SE
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 Wilo SE filed Critical Wilo SE
Publication of EP4343152A1 publication Critical patent/EP4343152A1/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
    • F04D1/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D1/06—Multi-stage 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
    • F04D13/00—Pumping installations or systems
    • F04D13/02—Units comprising pumps and their driving means
    • F04D13/021—Units comprising pumps and their driving means containing a coupling
    • 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
    • F04D13/10—Units comprising pumps and their driving means the pump being electrically driven for submerged use adapted for use in mining bore holes
    • 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
    • F04D29/426—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for liquid pumps
    • F04D29/4293—Details of fluid inlet or outlet
    • 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 invention relates to a vertical turbine pump with a riser pipe extending along an axis, a motor shaft arranged in the riser pipe, a motor arranged at an upper riser pipe end and driving the motor shaft, an impeller for conveying arranged at an opposite, lower riser pipe end and driven by the motor shaft a fluid into the riser pipe, and a tubular bend connected to the riser pipe at a first manifold end facing the impeller with an outlet at an opposite second manifold end for the conveyed fluid.
  • Vertical turbine pumps also known as vertical turbines, semi-axial pumps or borehole pumps, are vertical pumps that are used, for example, for wells and boreholes and are used in particular in industrial environments. Delivery heights of, for example, 40 to 100 meters can be achieved by connecting several impellers in series.
  • Vertical turbine pumps typically include a motor mounted on some type of base or motor mount.
  • a motor shaft can either be attached directly to the motor or coupled to it, and extends downward toward an impeller through a column bracket or a vertical tube assembly, also called a riser.
  • the impeller contains several impeller blades that rotate with the motor and the motor shaft, thus conveying the fluid into the riser pipe below.
  • EP 2606238 A1 a vertical pump elongated along a longitudinal direction, having a motor and rotatably coupled to the motor Motor shaft that drives an impeller.
  • the motor is arranged above the base plate, while in the mentioned delivery heights of, for example, 40 to 100 meters, the impeller is arranged at a corresponding distance below the base plate. In the event of a defect or maintenance, it is extremely time-consuming to pull the riser pipe with the impeller out of the borehole.
  • the known elbows are a manufactured construction in which round pieces of pipe are welded together, which is disadvantageous.
  • the manifold is usually welded to the so-called 'delivery bend & motor stool', DBMS, housing, which is arranged on the base plate and at the upper end of which the often very heavy motor is provided.
  • the seal housing provided on an upper side of the curved elbow, through which the motor shaft enters the riser pipe, essentially determines the vertical height of the DBMS housing.
  • the welded construction of the manifold leads to a large distance between the seal housing and the base plate and thus to a large height of the DBMS housing, which has a negative effect on the rigidity and natural frequency of the vertical turbine pump.
  • a pressure and often also a flow of the pumped fluid are usually measured at an outlet of the manifold.
  • the welded design of the manifold regularly leads to an angular shape within the manifold. This angular shape and a possible flow restriction through the seal housing cause turbulence at the outlet. In addition to affecting the hydraulic properties of the vertical turbine pump, the turbulence makes measurement very difficult and often leads to incorrect readings.
  • the manifold can be designed in the manner of a 'cobra head', namely the height of the manifold between the two manifold ends is reduced.
  • This allows the distance between the motor and a base plate to be reduced, which has a positive effect on the stiffness and natural frequency, and of course also on the manufacturing costs of the vertical turbine pump.
  • the proposed vertical turbine pump is less susceptible to vibration, which improves the operational stability of the vertical turbine pump.
  • the lower vertical height makes the vertical turbine pump easier to maintain or repair, as it is easier to accept the engine and/or the manifold, particularly above ground, if necessary.
  • the manifold with a reduced height between the two manifold ends reduces possible turbulence at the outlet, which has a positive effect on the measurement accuracy of pressure and flow of a sensor provided at the outlet.
  • the proposed manifold also improves the hydraulic properties of the vertical turbine pump.
  • the riser pipe can have an outside diameter of up to a few centimeters, so that the vertical turbine pump is often significantly longer axially along the axis than it is radially wide.
  • the riser pipe regularly extends mostly below the base plate on which the vertical turbine pump can be attached.
  • the motor and the manifold are preferably arranged above the base plate in such a way that the riser pipe is connected to the first manifold end in a fluid-tight manner just above or on the base plate and the motor is arranged vertically above the manifold.
  • the riser pipe is preferably made of metal and/or has a circular or circular cross section.
  • the motor shaft preferably extends in the axial direction along the center line of the riser pipe and, for this purpose, passes through the tubular elbow on an outside in an axial extension of the riser pipe.
  • An opening in the manifold can be provided on this outside, through which the motor shaft passes.
  • a seal in particular a radial seal, is preferably provided, which is arranged in the opening and seals the motor shaft in a fluid-tight manner from the manifold in a radially circumferential manner.
  • the riser pipe and/or the vertical turbine pump preferably has an axial longitudinal extent of ⁇ 10, 20, 30, 40 m, or more.
  • a plurality of impellers arranged axially one behind the other can be provided, through which the fluid is conveyed into the riser pipe and axially upwards towards the manifold.
  • the second riser pipe end is preferably connected to the first manifold end in a fluid-tight manner, in particular screwed.
  • the motor can be provided axially offset from the upper end of the riser pipe, as described below.
  • the elbow is preferably designed as a pipe bend or like a pipe bend and/or has a circular arc-like or elliptical shape in side view.
  • the elbow preferably extends over a circular arc or in the shape of a circular arc over 90°, although other values such as 80° or 100° are also possible.
  • the feature that the elbow has a curvature continuously away from the axis does not mean that the elbow initially extends in a direction opposite to the second end of the elbow, for example has an S-shaped shape, but rather linearly and / or continuously, especially in side view, circular arc-like or elliptical, extending continuously further away from the axis or the riser pipe with respect to its radial center line.
  • the feature that the manifold has a curvature continuously away from the axis is to be understood in particular as synonymous with the feature that the manifold extends continuously away from the axis with respect to its radial, in particular circular arc-like, center line.
  • the minor axis of the ellipse preferably runs parallel to the axis and/or the major axis runs horizontally.
  • the radial diameter as the height of the manifold initially reduces and then increases from the first manifold end to the second manifold end means in particular that at at least one position between the first manifold end and the second manifold end the height of the manifold is less than the height at the first manifold end and/or at the second manifold end.
  • the manifold has a particularly 'flattened' shape.
  • the manifold can have a 'dimpled' shape on its outside when viewed from the side, with the height at the 'dent' being reduced to a maximum.
  • the radial diameter is understood to mean, in particular, a radial inner diameter of the elbow, which defines a clear height in the elbow through which the fluid can flow.
  • the outside diameter can also be meant in addition to the inside diameter.
  • the radial diameter initially decreases and then increases steadily.
  • the radial diameter can decrease and/or increase continuously, although it is also possible for the radial diameter to remain constant in some areas in order to subsequently decrease and/or increase.
  • the radial diameter does not decrease and/or increase in a sudden manner, but in particular linearly.
  • the radial diameter between the first manifold end and the second manifold end decreases compared to the radial diameter at the first manifold end and/or at the second manifold end by ⁇ 10%, 20%, 30%, 40%, 50% or 60% reduced.
  • the height of the manifold can be 40% of the height at the first manifold end and/or at the second manifold end, with the height decreasing linearly up to the minimum height and then can increase linearly again.
  • an axial diameter as the width of the manifold initially increases from the first manifold end to the second manifold end and then decreases.
  • the width of the manifold is greater than the width at the first manifold end and/or at the second manifold end.
  • the elbow In plan view, in particular in the direction of a radius of the elbow, the elbow has a widespread shape, particularly in the middle of its extent.
  • the manifold can again have a bulge when viewed from above have, with the width being increased to the maximum at the axial 'bump'.
  • the axial diameter is understood to be, in particular, an axial inner diameter of the elbow, which defines a clear width within the elbow through which the fluid can flow.
  • the axial diameter initially increases steadily and then decreases steadily.
  • the axial diameter can increase and/or decrease continuously, although it is also possible for the axial diameter to remain constant in some areas in order to subsequently increase and/or decrease.
  • the axial diameter does not increase and/or decrease suddenly, but rather linearly.
  • the axial diameter between the first manifold end and the second manifold end increases by ⁇ 10%, 20%, 30%, 40%, 50% compared to the radial diameter at the first manifold end and/or at the second manifold end. 60%, 70% or 80%.
  • the width of the manifold can be 180% of the width at the first manifold end and/or at the second manifold end, with the width increasing linearly up to the maximum height and then can decrease linearly again.
  • the manifold is designed in the manner of a cobra head, particularly in perspective view.
  • a cobra head is characterized by a wider shape with a lower height than a cobra body with a circular cross-section, i.e. in particular by a height of the manifold, which initially decreases from the first manifold end towards the second manifold end and then increases, as well as by a width of the manifold, which initially increases and then decreases from the first manifold end to the second manifold end.
  • the cobra head in question does not have an S-shaped shape when viewed from the side, but rather always extends away from the axis with respect to its center line.
  • a cross section of the manifold is always the same size in the course between the first manifold end and the second manifold end. This means that if the height of the manifold decreases between the first manifold end and the second manifold end, the width of the manifold increases accordingly.
  • a drive lantern with a coupling provided between the motor and the motor shaft is arranged between the engine and the manifold, the drive lantern and the manifold, including a manifold housing preferably having the manifold, being designed in two parts.
  • the drive lantern and/or the manifold housing preferably have a rectangular cross section in plan view and/or are designed like a cuboid.
  • the manifold housing is preferably mounted in a stationary manner on the base plate or the like, in particular screwed.
  • the riser pipe preferably extends vertically and/or axially below the base plate and is preferably also mounted in a stationary manner, in particular screwed, to the base plate and/or the manifold housing.
  • the drive lantern is preferably fixed in place in an axial extension of the riser pipe between the manifold housing and the engine, in particular screwed to the manifold housing and the engine.
  • the bend has a constantly changing elliptical cross-section between the first bend end, which has a particularly circular cross-section, and the second bend end, which has a particularly circular cross-section.
  • the minor axis of the elliptical cross-section extends in the radial direction relative to the bend as the height of the bend, while the major axis of the elliptical cross-section extends orthogonally thereto as the width of the bend.
  • the first bend end and the second bend end have an equally large, in particular circular, cross-section.
  • a radius of a radial inner manifold edge increases in particular continuously from the first manifold edge towards the second manifold edge.
  • the curvature of the radial inner manifold edge i.e. in particular also of the manifold, flattens or decreases in particular steadily from the first manifold edge towards the second manifold edge.
  • the manifold can be designed with a low height relative to the axis of the riser pipe, which moves the engine closer to the base plate, so that vibrations are reduced, which leads to more stable operation of the vertical turbine pump.
  • the manifold is made of gray cast iron.
  • the manifold housing including the manifold is preferably made of gray cast iron.
  • Gray cast iron is understood to mean in particular gray cast iron, i.e. a group of iron-carbon alloys with a high proportion of carbon, in particular > 2%, the carbon being in the form of graphite.
  • silicon can be included to improve castability, as well as other alloy components such as manganese, chromium or nickel.
  • the proposed manifold and thus the vertical turbine pump can be manufactured much more simply and cost-effectively.
  • Fig. 1 shows a schematic sectional view of a vertical turbine pump 1 with a manifold housing 2 having a manifold 3 according to a preferred embodiment of the invention.
  • the vertical turbine pump 1 has a riser pipe 5 that extends along an axis 4 and has a circular outer cross section and has a plurality of interconnected segments.
  • a motor shaft 6 extends along the axis 4 and along the entire length of the riser 5 in such a way that a free space is formed radially around the motor shaft 6 between it and the riser 5, through which the vertical turbine pump 1 pumped fluid rises axially upwards.
  • several impellers 8 arranged axially one above the other are provided at a lower end of the riser pipe 7, which are driven by the motor shaft 6, suck in the fluid and convey it into the free space.
  • the riser pipe 5 is attached with its upper riser pipe end 9 to a base plate 10, so that the riser pipe 5 extends vertically downwards away from the base plate 10.
  • the manifold housing 2 Above the base plate 5, vertically or in the direction of the axis 4, the manifold housing 2 is connected, which in turn is axially connected by a drive lantern 11 and finally a motor 12 driving the motor shaft 6.
  • a clutch 13 is arranged in the drive lantern 11 and is connected between the motor 12 and the motor shaft 6.
  • the manifold housing 2 and the drive lantern 11 are designed in two parts and screwed together.
  • the upper riser pipe end 9 is fluid-tight a first manifold end 14 of the manifold 3 facing the impeller 8.
  • Fig. 2 which shows a schematic sectional view of the manifold housing 2 having the manifold 3 according to the preferred exemplary embodiment of the invention
  • the manifold 3 has an outlet 16 for the conveyed fluid at a second manifold end 15 arranged opposite the first manifold end 14.
  • the tubular elbow 3 redirects the conveyed fluid from the vertical to the horizontal, so that cross-sectional surfaces at the first elbow end 14 and the second elbow end 15 are arranged offset from one another by 90 °.
  • the inner cross-sectional areas of the two manifold ends 14, 15 are, on the one hand, the same size and, on the other hand, circular.
  • the manifold 3 shown radial center line 17 of the manifold 4, designated in the one showing the manifold 3 in a schematic side view Fig. 3 as a cutting line BB, the manifold 3 extends from the first manifold end 14 steadily away from the axis 4 towards the second manifold end 15.
  • the radial inner diameter of the manifold 3 is reduced by 40% approximately in the middle between the first manifold end 14 and the second manifold end 15.
  • other ratios such as 30%, 50%, 20% or 60% are possible.
  • Motor shaft 6 not shown, which corresponds to an outer wall of the manifold 3 Fig. 2 Opening shown, also called cut-out, enters the manifold 3 in the area of the axis 4.
  • the motor shaft 6 is sealed in this opening from the outer wall by means of a seal, not shown, which seal can protrude into the manifold 3, but is not considered a reduction in the radial inner diameter in the sense of the feature described above.
  • FIG. 4 shows a schematic sectional view of the manifold housing 2 having the manifold 3 through the section line BB according to the preferred exemplary embodiment of the invention, i.e. along the center line 17 of the manifold 3.
  • other ratios such as 20%, 40%, 10% or 50% are possible.
  • the manifold 3 is designed in the manner of a cobra head, i.e. along its arcuate extension from the first manifold end 14 to the second manifold end 15, in side view, on the one hand flattened and on the other hand, in plan view, widened.
  • the manifold 3 is further designed such that a radius of a radial inner manifold edge 18 of the manifold 3 increases steadily in the course from the first manifold edge 15 towards the second manifold edge 15.
  • the radial inner bend edge 18 flattens less and less as the course increases, that is, the curvature decreases as the course increases.
  • the result is a lower height of the elbow 3 relative to the axis 4 compared to a course with the same curvature.
  • the curved manifold 3 described including the manifold housing 2 which accommodates the manifold 3 and has a rectangular shape in plan view, are made of gray cast iron.
  • the manifold 3 is manufactured by means of a mold (not shown) for casting the manifold 3 in such a way that when the manifold 3 produced is connected to the riser pipe 3 at the first manifold end 14 facing the impeller 6, the manifold 3 is different in terms of its shape radial center line 17 extends steadily away from the axis 4, at the opposite second elbow end 15 the outlet 16 for the conveyed fluid is provided, and the radial diameter as the height of the elbow 3 initially decreases from the first elbow end 14 towards the second elbow end 15 and then enlarged as previously described.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Mining & Mineral Resources (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
EP23193820.0A 2022-09-20 2023-08-29 Pompe à turbine verticale Pending EP4343152A1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
BE20225745A BE1030893B1 (de) 2022-09-20 2022-09-20 Vertikale Turbinenpumpe

Publications (1)

Publication Number Publication Date
EP4343152A1 true EP4343152A1 (fr) 2024-03-27

Family

ID=83689753

Family Applications (1)

Application Number Title Priority Date Filing Date
EP23193820.0A Pending EP4343152A1 (fr) 2022-09-20 2023-08-29 Pompe à turbine verticale

Country Status (3)

Country Link
EP (1) EP4343152A1 (fr)
CN (1) CN221647194U (fr)
BE (1) BE1030893B1 (fr)

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2002195185A (ja) * 2000-12-25 2002-07-10 Dmw Corp 立軸ポンプ
US20020164245A1 (en) * 2001-04-05 2002-11-07 Tomoyoshi Okamura Pump
JP2013024037A (ja) * 2011-07-15 2013-02-04 Dmw Corp 立軸ポンプ
EP2606238A1 (fr) 2010-08-17 2013-06-26 MPC Inc. Pompe à turbine verticale non métallique
JP2013209961A (ja) * 2012-03-30 2013-10-10 Ebara Corp 剥離防止構造体を備えたポンプ装置

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2002195185A (ja) * 2000-12-25 2002-07-10 Dmw Corp 立軸ポンプ
US20020164245A1 (en) * 2001-04-05 2002-11-07 Tomoyoshi Okamura Pump
EP2606238A1 (fr) 2010-08-17 2013-06-26 MPC Inc. Pompe à turbine verticale non métallique
JP2013024037A (ja) * 2011-07-15 2013-02-04 Dmw Corp 立軸ポンプ
JP2013209961A (ja) * 2012-03-30 2013-10-10 Ebara Corp 剥離防止構造体を備えたポンプ装置

Also Published As

Publication number Publication date
CN221647194U (zh) 2024-09-03
BE1030893B1 (de) 2024-04-15
BE1030893A1 (de) 2024-04-12

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