EP4305317A1 - Pompe centrifuge présentant des ailettes d'entrée - Google Patents

Pompe centrifuge présentant des ailettes d'entrée

Info

Publication number
EP4305317A1
EP4305317A1 EP22711543.3A EP22711543A EP4305317A1 EP 4305317 A1 EP4305317 A1 EP 4305317A1 EP 22711543 A EP22711543 A EP 22711543A EP 4305317 A1 EP4305317 A1 EP 4305317A1
Authority
EP
European Patent Office
Prior art keywords
inlet
ribs
centrifugal pump
profile
thickness
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
EP22711543.3A
Other languages
German (de)
English (en)
Inventor
Oliver Schuster
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.)
KSB SE and Co KGaA
Original Assignee
KSB SE and Co KGaA
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 KSB SE and Co KGaA filed Critical KSB SE and Co KGaA
Publication of EP4305317A1 publication Critical patent/EP4305317A1/fr
Pending legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2240/00—Components
    • F05D2240/10—Stators
    • F05D2240/12—Fluid guiding means, e.g. vanes
    • F05D2240/126—Baffles or ribs
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2250/00—Geometry
    • F05D2250/20—Three-dimensional
    • F05D2250/26—Three-dimensional paraboloid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2250/00—Geometry
    • F05D2250/50—Inlet or outlet
    • F05D2250/51—Inlet

Definitions

  • the invention relates to a centrifugal pump arrangement with a flydraulic housing having an inlet opening for sucking in a pumped medium and an outlet opening for ejecting the pumped medium, wherein at least two inlet ribs are provided in the inlet opening with one end facing the delivery flow flowing into the inlet opening and one end facing away from the delivery flow .
  • the housing or inflow parts of centrifugal pumps are often equipped with so-called inlet ribs.
  • Their task is, on the one hand, to reduce the so-called pre-swirl or part-load vortices, and on the other hand to ensure an almost axial inflow.
  • One advantage that comes with this is the stable development of the delivery height characteristics. Instabilities are almost completely prevented at partial load and overload. Furthermore, a break in the characteristic curve in the case of disproportionately large volume flows is counteracted, which increases the range of application of the pump. A relatively wide geometry of the inlet ribs with pronounced curves on the upper side is essential for this.
  • inlet ribs A suitable choice of rib size, rib geometry and number of ribs is decisive for the proper function of the inlet ribs.
  • inlet or suction flange diameter of up to DN100, two opposing ribs are used.
  • three ribs are usually used, which are offset by 120°.
  • Inlet ribs also have a significant influence on the cavitation behavior of the impeller and thus significantly influence the NPSH value. Therefore, both the number and the geometric design as well as the aerodynamic profile of these ribs are of great importance, since otherwise unfavorable NPSH values are the result.
  • DE 1 161 481 B describes a device for stabilizing the characteristic (VH characteristic) of centrifugal wheel machines in which the inlet is provided with an additional rib in order to improve the part-load operating behavior and reduce the part-load characteristic instability.
  • the primary goal is not to improve the NPSH value.
  • US Pat. No. 2,219,390 A describes an impeller that is installed in a housing with inlet ribs, the inlet ribs not having any particular characteristics with regard to NPSH optimization.
  • the object of the invention is to develop an NPSH-friendly solution for inlet ribs, which avoids the above-mentioned disadvantages and risks with the simplest production technology.
  • the solution according to the invention provides that the thickness profile of the at least two inlet ribs changes from the end facing the conveying flow to the end facing away from the conveying flow. It is particularly advantageous that both the number and position of the inlet ribs and their original dimension in terms of length and height can be retained. As a result, the advantages described above with regard to pre-swirl and part-load vortices continue to be ensured. Only the configuration of the rib thickness has to be adjusted.
  • the configuration of the rib thickness and the optimization of the thickness profile result in an optimized profile in terms of suction technology, which avoids cavitation at the start of the rib and leads to the suction flow being applied to the inlet rib.
  • As a result less energy is withdrawn from the sucked liquid flow, which would otherwise convert into cavitation, but now remains in the medium.
  • By suppressing cavitation and the associated cavitation bubbles a severe narrowing of the usable flow cross section is prevented.
  • an increased feed rate with concurrent static pressure drop is also avoided. The result is an improved suction capability of the pump.
  • the thickness profile of the inlet ribs changes from the start of the rib to the end of the rib, namely in the form of a fish-belly profile, in order to improve the contact of the suction flow with the inlet rib.
  • the thickness of the inlet rib increases along a skeleton line up to a defined relative length of the profile in a parabola-like manner and from there to the end facing away from the flow.
  • Such a geometry can be reproduced in the casting process, for example.
  • the inlet ribs can also be machined mechanically to achieve the required geometry.
  • the start of the rib is rounded in order to avoid or minimize the occurrence of rib cavitation at the start of the rib.
  • the rib end is designed with a radius that is as small as possible in order to take the fish belly profile into account as best as possible and to improve the outflow of the fluid.
  • a sharp-edged design of the ribs has proven to be particularly advantageous.
  • the relative profile thickness advantageously reaches a value of 0.060 for a relative profile length of 0.25.
  • the thickness profile of the inlet ribs may deviate constantly over the entire length of the inlet ribs by a specific thickness factor from the ideal thickness profile of the inlet ribs.
  • the thickness factor is calculated as follows: 1+(thickness deviation of the profile for NPSH inlet rib in % / 100%).
  • a maximum thickness factor of 1.3 has proven to be particularly advantageous in investigations and test runs.
  • Fig. 3 is a schematic representation of the ideal profile of the inlet rib in centrifugal pumps.
  • Fig. 1 shows a sectional view of an exemplary pump arrangement in the form of a centrifugal pump with a housing 1.
  • the housing 1 comprises a hydraulic housing 2, a housing cover 3 and a bearing bracket 4.
  • the hydraulic housing 2 has an inlet opening 5 for sucking in a pumped medium and an outlet opening 6 for ejecting the pumped medium.
  • At least two inlet ribs 7 are provided in the area of the inlet opening 5 .
  • a shaft 8 extends from a limited by hydraulic housing 2 and housing cover 3 flow chamber 9 through the housing cover 3 and through the bearing carrier 4, which is attached to the housing cover 3 on the side facing away from the flow chamber 9 th side.
  • a housing cover 3 is arranged close to the first bearing 10 and a housing cover 3 distant from the second bearing 11, which supports the shaft 8.
  • the shaft 8 has an axially extending axis of rotation A and carries at a first end 12 an impeller 13 which rotates about the axis of rotation A together with the shaft 8 .
  • the impeller 13 is located in the flow chamber 9 delimited by the hydraulic housing 2 and the housing cover 3.
  • a second end 14 of the shaft 8 opposite the first end 12 extends out of the bearing carrier 4.
  • a motor is provided at the free end 14 extending out of the bearing carrier 4, which rotates the shaft 8 about the axis of rotation A rotatably drives.
  • the impeller 13 is designed as a radial impeller.
  • FIG. 2 shows the hydraulic housing 2 with two inlet ribs 7 profiled according to the invention with an end 15 facing the delivery flow Fs flowing into the inlet opening 5 and an end 16 facing away from the delivery flow.
  • Fig. 3 shows a schematic representation of a thickness profile 17 of the inlet rib 7 according to the invention from the end 15 facing the delivery flow Fs along a skeleton line X to an end 16 facing away from the delivery flow.
  • the skeleton line X runs essentially parallel to the axis of rotation A.
  • the thickness of the inlet rib 7 increases along the skeleton line X in a parabola shape up to a defined relative length of the profile and then decreases again towards the end 16 facing away from the delivery flow Fs.
  • the relative profile thickness reaches a value of 0.016, with a relative profile length of 0.025, the relative profile thickness reaches a value of 0.027, with a relative profile length of 0.05, the relative profile thickness reaches a value of 0.035, with a relative profile length of 0.1, the relative profile thickness reaches a value of 0.048, with a relative profile length of 0.15, the relative profile thickness reaches a value of 0.054, with a relative profile length of 0.2, the relative profile thickness reaches a value of 0.059, with a relative profile length of 0.25, the relative profile thickness reaches a value of 0.060 , with a relative profile length of 0.3 the relative profile thickness reaches a value of 0.058, with a relative profile length of 0.4 the relative profile thickness reaches a value of 0.055, with a relative profile length of 0.5 the relative profile thickness reaches a value of 0.051, with a relative profile length of 0.6 the relative profile thickness reaches a value of
  • the rib end is preferably designed with sharp edges.
  • the inlet rib 7 has a typical fish-belly profile.
  • Such an optimized profile helps to avoid cavitation at the start of the ribs and ensures that the fluid flow rests against the inlet rib 7.
  • Fliering means that less energy is withdrawn from the sucked-in liquid flow Fs, which would otherwise convert into cavitation, but now remains in the medium.
  • an increased feed rate with concurrent static pressure drop is also avoided. The result is an improved suction capability of the pump.
  • the inlet ribs 7 can be produced, for example, with the casting of the hydraulic housing 2 and/or by means of additive manufacturing. However, the inlet ribs 7 can also be attached to the hydraulic housing 2 subsequently by welding or another fastening method.

Landscapes

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

Abstract

L'invention se rapporte à un ensemble pompe centrifuge, comprenant un boîtier hydraulique, qui présente une ouverture d'entrée destinée à recevoir un milieu transporté et une ouverture de sortie destinée à évacuer le milieu transporté, au moins deux ailettes d'entrée ayant une extrémité faisant face au flux transporté s'écoulant dans l'ouverture d'entrée et une extrémité opposée au flux transporté étant disposées dans l'ouverture d'entrée. Selon l'invention, le profil d'épaisseur (17) des deux, ou plus, ailettes d'entrée (7) change depuis l'extrémité (15) faisant face au flux transporté (Fs) jusqu'à l'extrémité (16) opposée au flux transporté.
EP22711543.3A 2021-03-10 2022-03-09 Pompe centrifuge présentant des ailettes d'entrée Pending EP4305317A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102021105727.2A DE102021105727A1 (de) 2021-03-10 2021-03-10 Kreiselpumpe mit Einlaufrippen
PCT/EP2022/056004 WO2022189489A1 (fr) 2021-03-10 2022-03-09 Pompe centrifuge présentant des ailettes d'entrée

Publications (1)

Publication Number Publication Date
EP4305317A1 true EP4305317A1 (fr) 2024-01-17

Family

ID=80819697

Family Applications (1)

Application Number Title Priority Date Filing Date
EP22711543.3A Pending EP4305317A1 (fr) 2021-03-10 2022-03-09 Pompe centrifuge présentant des ailettes d'entrée

Country Status (3)

Country Link
EP (1) EP4305317A1 (fr)
DE (1) DE102021105727A1 (fr)
WO (1) WO2022189489A1 (fr)

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2219390A (en) 1938-09-12 1940-10-29 Duriron Co Centrifugal pump with dual impeller
DE1161481B (de) 1960-03-19 1964-01-16 Voith Gmbh J M Einrichtung zur Stabilisierung der Charakteristik von Kreiselradarbeitsmaschinen mit axialdurchstroemtem Laufrad
DE2243365C3 (de) 1972-09-02 1979-02-22 Klein, Schanzlin & Becker Ag, 6710 Frankenthal Selbsttätige Sicherheitsregelung für einen Reaktorkühlkreislauf
DE19510812A1 (de) 1995-03-24 1996-09-26 Klein Schanzlin & Becker Ag Kreiselpumpe
JP4573020B2 (ja) * 2004-05-06 2010-11-04 株式会社日立プラントテクノロジー 吸込ケーシング、吸込流路構造および流体機械
ATE511606T1 (de) 2008-10-01 2011-06-15 Grundfos Management As Kreiselpumpenaggregat
DE102018204503A1 (de) * 2018-03-23 2019-09-26 Robert Bosch Gmbh Flüssigkeitspumpe
CN210343860U (zh) * 2019-04-25 2020-04-17 浙江理工大学 一种带有角度可调仿生导叶的周向轴向可调节筒体
CN212250476U (zh) * 2020-05-13 2020-12-29 重庆水泵厂有限责任公司 一种核电用立式反冲洗水泵

Also Published As

Publication number Publication date
DE102021105727A1 (de) 2022-09-15
WO2022189489A1 (fr) 2022-09-15

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