WO2021023660A1 - Roue monocanal de pompe centrifuge fermée destinée à des fluides qui ont des mélanges abrasifs ou érosifs - Google Patents

Roue monocanal de pompe centrifuge fermée destinée à des fluides qui ont des mélanges abrasifs ou érosifs Download PDF

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Publication number
WO2021023660A1
WO2021023660A1 PCT/EP2020/071669 EP2020071669W WO2021023660A1 WO 2021023660 A1 WO2021023660 A1 WO 2021023660A1 EP 2020071669 W EP2020071669 W EP 2020071669W WO 2021023660 A1 WO2021023660 A1 WO 2021023660A1
Authority
WO
WIPO (PCT)
Prior art keywords
profile
blade
impeller
suction
thickness
Prior art date
Application number
PCT/EP2020/071669
Other languages
German (de)
English (en)
Inventor
Fritz JOCHEN
Christoph Jäger
Wolfgang Metzinger
Steffen Schmidt
Rolf Witzel
Original Assignee
KSB SE & 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 & Co. KGaA filed Critical KSB SE & Co. KGaA
Priority to CN202080069329.7A priority Critical patent/CN114423951A/zh
Priority to EP20753307.6A priority patent/EP4010598A1/fr
Publication of WO2021023660A1 publication Critical patent/WO2021023660A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/18—Rotors
    • F04D29/22—Rotors specially for centrifugal pumps
    • F04D29/24—Vanes
    • F04D29/242—Geometry, shape
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/18—Rotors
    • F04D29/22—Rotors specially for centrifugal pumps
    • F04D29/2205—Conventional flow pattern
    • F04D29/2222—Construction and assembly
    • F04D29/2227—Construction and assembly for special 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
    • F04D29/18—Rotors
    • F04D29/22—Rotors specially for centrifugal pumps
    • F04D29/2261—Rotors specially for centrifugal pumps with special measures
    • F04D29/2294—Rotors specially for centrifugal pumps with special measures for protection, e.g. against abrasion
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D7/00—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts
    • F04D7/02—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts of centrifugal type
    • F04D7/04—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts of centrifugal type the fluids being viscous or non-homogenous
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D7/00—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts
    • F04D7/02—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts of centrifugal type
    • F04D7/06—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts of centrifugal type the fluids being hot or corrosive, e.g. liquid metals
    • 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
    • F05D2240/20—Rotors
    • F05D2240/30—Characteristics of rotor blades, i.e. of any element transforming dynamic fluid energy to or from rotational energy and being attached to a rotor
    • F05D2240/301—Cross-sectional characteristics
    • 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
    • F05D2240/20—Rotors
    • F05D2240/30—Characteristics of rotor blades, i.e. of any element transforming dynamic fluid energy to or from rotational energy and being attached to a rotor
    • F05D2240/303—Characteristics of rotor blades, i.e. of any element transforming dynamic fluid energy to or from rotational energy and being attached to a rotor related to the leading edge of a rotor blade
    • 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
    • F05D2240/20—Rotors
    • F05D2240/30—Characteristics of rotor blades, i.e. of any element transforming dynamic fluid energy to or from rotational energy and being attached to a rotor
    • F05D2240/305—Characteristics of rotor blades, i.e. of any element transforming dynamic fluid energy to or from rotational energy and being attached to a rotor related to the pressure side of a rotor blade

Definitions

  • the invention relates to a closed centrifugal pump channel impeller for liquids with abrasive or erosive admixtures, consisting of a support and a cover disk and one or more blades arranged in between ...
  • centrifugal pumps are often used for pumping media with components that promote wear. Wear occurs primarily on the components of the pump that come into contact with the flow. These include in particular the impeller, any stator, the pump housing with attachments and housing covers, but also the shaft seal.
  • the wear or the material removal rate depends strongly on the local flow velocity.
  • the pump impeller is particularly badly affected by this, because particularly high speeds occur when the air flows around the impeller blades.
  • catfish approaches One possibility is to coat the affected surfaces with elastomers such as rubber or polyurethane of low hardness.
  • the elastomer coating absorbs the impact energy of the solid particles contained in the conveying medium, which means that they do not damage the components or damage them less.
  • Another possibility is the use of component materials whose hardness is greater than the hardness of the solids contained in the conveying medium. Both metallic and non-metallic materials can be considered as materials with great hardness.
  • the pump components, in particular the impeller are essentially manufactured using primary molding processes.
  • components made of alloyed steels are created using conventional foundry processes and then mechanically reworked.
  • the above-described process for component production is comparatively expensive, the additional costs result mainly from the energy-intensive casting process, but also from the metallic alloy components.
  • a particularly wear-critical location is the leading edge of the impeller.
  • wear can progress to such an extent that the impeller blades are largely worn away.
  • this can lead to a collapse in the delivery rate.
  • the cover plate can become detached, which leads to a complete destruction of at least the impeller.
  • Impellers made of polymer with silicon carbide inclusions are particularly affected by this type of destruction, since both the tensile strength and the breaking strength of plastics with silicon carbide inclusions are significantly lower than those of a steel alloy. Even comparatively little wear can lead to total failure of the impeller.
  • the application deals with the above problem and tries to show possible solutions that can reduce material wear through an optimized design of the impeller. This object is achieved by an impeller according to the features of claim 1.
  • Advantageous embodiments of the impeller are the subject of the dependent claims.
  • the aim of the invention is to minimize and delay the wear and tear of the leading edge of the impeller, so that the service life of the impeller is increased. According to the invention, this is achieved by a special profiling of at least one of the impeller inlet edges.
  • the main aim is to reduce the sensitivity of the leading edge to incorrect flow and to reduce the velocity gradient when the flow around the leading edge from the pressure side to the suction side at partial-load operating points.
  • the suction and pressure side of the vane is created by placing the vane profile with a vane thickness s d on the pressure side and with the vane thickness s s on the suction side on an existing skeleton surface, resulting in a total vane thickness.
  • the starting point for this are sketches for the profiling on the support disk (hub, pressure-side cover disk) and on the cover disk (suction-side cover disk).
  • at least one blade in the interface area to the support and / or cover disk has a blade profile shape that is asymmetrical with respect to the skeleton line.
  • the asymmetry is achieved by placing a different blade thickness / profile thickness on the pressure and suction side, in other words the thickness of the blade profile from the camber line to the suction-side or pressure-side edge of the blade is different, so that with respect to the camber line an asymmetry is present as a line of symmetry at least for partial areas over the blade length, ie in the direction from the inlet to the outlet edge.
  • the channel wheel is made of a cast or otherwise molded material, for example steel or mineral casting.
  • the impeller can also be made of polymers wear-resistant embedded particles, e.g. fine-grain silicon carbides (SiC).
  • the suction-side blade Z-profile thickness is greater than the pressure-side blade Z-profile thickness.
  • the asymmetrical blade thickness of the suction and pressure side preferably extends only over a limited area of the blade length; there is quasi a regional thickening of the blade profile on its suction side.
  • Such a thickening is preferably provided with a relative blade length of 10% -50% starting from the leading edge.
  • the greatest difference in thickness is particularly preferably provided in the range of 5% -15% of the relative blade length, ideally around 10% of the relative blade length.
  • the profile thickness in the area of the suction-side thickening at the interface with the support disk is 20% to 40% higher than the profile thickness in the area of the outlet edge of the suction side.
  • the aforementioned asymmetry or thickening comprises a size ratio of the suction-side to the pressure-side profile thickness of at least 1.3-1.8. If there is a thickening on the suction side of the blade, the size ratio increases, for example, starting from the leading edge until a maximum value in the aforementioned range between 1.3-1.8 is reached. The size ratio then decreases again in the direction of the trailing edge. It can be sensible for a relative blade length of approximately 20% -30%, in particular approximately 25%, to have a size ratio of at least 1.3, preferably at least 1.4.
  • the shape of the impeller leading edge is elliptically profiled, in particular the profile shape of the leading edge is formed by two partial ellipses merging tangentially into one another at the leading edge point with an elliptical angle of at least 90 ° to a maximum of 180 °.
  • the leading edge shows a quarter-ellipse shape in the transition to the pressure side, which is then divided by a constant profile width up to the trailing edge.
  • the transition from the inlet edge point to the suction side is formed by an ellipse with an ellipse angle greater than 90 ° so that the ellipse shape forms the section-wise thickening and then drops to a constant profile thickness up to the exit edge.
  • This has the advantage that the transition from the largest suction-side profile thickness to a profile thickness that remains almost constant in the direction of the impeller outlet edge is formed by a kink-free curve (ellipse angle> 90 °).
  • leading edge point can be shifted from the skeleton line or skeleton surface of the blade in the direction of the pressure side or in the direction of the suction side.
  • the asymmetrical blade profile shape in particular the aforementioned thickening on the suction side, can extend from the support disk to the cover disk.
  • a profile shape that changes between the support disk and cover disk is also conceivable.
  • an asymmetrical blade profile shape is only provided in the interface area with the support disk.
  • the leading edge profile can be formed by two quarter ellipses which merge tangentially into one another at the entry edge point there.
  • the ratio of the total profile thickness of the blade in the area of the carrier and cover disk with a common radial beam from a relative blade length of 8% - 12% has a ratio of 1, 08 to 1.12.
  • FIG. 1 a perspective view of the suction side of the invention
  • FIG. 2 a detailed representation of the blade shape according to the invention
  • FIG. 3 a profile representation of the impeller blade according to FIG. 2 in the area of its transition to the support disk
  • Figures 4a, b a modified embodiment according to Figure 3 and
  • Figures 5a, b Profile representation of the blade in the area of the cover disk.
  • FIG. 1 shows a perspective view of the centrifugal pump channel impeller according to the invention.
  • the impeller is designed as a closed channel impeller with a cover plate 1 and a support plate 2.
  • Several blades 3 extend between the support and cover disks.
  • the blades 3 are delimited in the direction of flow by their leading edge (suction edge) 3a and their trailing edge (pressure edge) 3b. Transverse to the direction of flow, they are delimited by the cover and support disks 1, 2.
  • the channel wheel is made of a cast or otherwise formable material, such as steel or mineral casting.
  • the impeller can also consist of polymers with wear-resistant embedded particles, for example fine-grain silicon carbides (SiC).
  • SiC fine-grain silicon carbides
  • the wear resistance of the impeller and thus its achievable runtime performance is optimized by a special profiling of the impeller leading edges 3a. Due to the new profiling, the sensitivity of the leading edges to incorrect flow can be reduced by reducing the speed gradient of the The resulting fluid flow around the inlet edges 3a from the pressure side B to the suction side A is reduced at partial-load operating points.
  • the suction and pressure side of the blade 3 is created by placing the blade profile on an existing skeleton surface 5 with the blade thickness s d on the pressure side B and the blade thickness s s on the suction side A. The result is a total blade thickness of s, which is in blade lengths - direction varies. This can be seen in FIGS. 2, 3, FIG. 3 here showing the profile shape of the blade 3 in the area of the support disk 2.
  • the length of the profiling on the pressure side is referred to here as X ed .
  • the blade profile on the suction side A is thickened over a length of X to a dimension Y in relation to the blade thickness of the leading edge 3a. In this case, the thickening on the suction side reaches its greatest profile thickness at a length of X es as seen from the leading edge 3a.
  • the profile thickness s s decreases in the direction of the trailing edge 3b in the form of a kink-free curve until the profile thickness s s , which remains constant up to the trailing edge, is reached.
  • the profile shape from the leading edge point 3c to the greatest thickness at point X es and to the point where the profile thickness remains constant can also be described as a partial ellipse with an ellipse angle of a A.
  • the two ellipses of the pressure side B and the suction side A merge tangentially into one another at the leading edge 3a at the leading edge point 3c.
  • FIG. 4 a shows the blade profile in the area of the support disk 2.
  • the leading edge point 3c on the suction side A is shifted by the amount y es from the skeleton surface 5 in the direction of the suction side A.
  • a displacement of the leading edge point 3c by the amount y ed in the direction of the pressure side B is also possible, as shown in FIG. 4b.
  • Said thickening according to the above exemplary embodiments can extend from the support disk 2 to the cover disk 1. In another embodiment, this thickening is only arranged on the support disk 2.
  • the profile on the cover disk 1 also consists of two quarter ellipses which merge tangentially into one another at the entry edge.
  • the transition point 3c at the leading edge 3a can lie above (see FIG. 5b) or below (see FIG. 5a) the center 10 of the blade profile, which results in an asymmetrical profile of the leading edge 3a.
  • the material thickness ratio between the carrier disk and the cover disk 2, 1 can have a ratio of 1.08-1.12 from a relative blade length of 10%, the maximum blade thickness on the carrier disk 2 at a relative blade length of 0.25 has at least a ratio of 1.425.
  • the maximum blade thickness on the support disk 2 is reached at 10% of the length of the skeleton line 10 on the suction side.
  • the vane thickness of the suction-side thickening is 20% - 45% higher than the vane thickness in the exit area of this flow filament.
  • the profile thickening, as described above for the support disk 2 is arranged only on the profile of the cover disk 1, while the profile on the support disk 2 is designed as described above for the cover disk 1.
  • the profiles on the support and cover plate 2, 1 can have the same geometric parameters. However, if the profiles on the support and cover plate 2, 1 are designed differently - as described above - then the profiles should merge evenly into one another above the blade height.
  • the spatial profiling of the impeller blades according to the invention minimizes cavitation by minimizing shear stress on the blade surface, which in impellers made of polymer cast with silicon carbide significantly reduces surface wear. Also, detachments in the design area that negatively affect energy conversion are avoided.
  • the special profiling reduces the wear caused by abrasion and cavitation erosion and at the same time increases the energy conversion and thus the efficiency of such an impeller.

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

Abstract

L'invention concerne une roue monocanal de pompe centrifuge fermée destinées à des fluides qui présentent des mélanges abrasifs ou érosifs, constituée d'un disque de support et d'un disque de couverture et d'une ou de plusieurs lames disposées entre ces dernières, caractérisée en ce que, dans la zone d'interface avec le disque de support et/ou le disque de couverture, au moins une lame présente une forme de profil de pale asymétrique par rapport à la ligne de cambrure.
PCT/EP2020/071669 2019-08-05 2020-07-31 Roue monocanal de pompe centrifuge fermée destinée à des fluides qui ont des mélanges abrasifs ou érosifs WO2021023660A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
CN202080069329.7A CN114423951A (zh) 2019-08-05 2020-07-31 用于具有磨蚀性的或侵蚀性的混合物的液体的闭合式离心泵通道叶轮
EP20753307.6A EP4010598A1 (fr) 2019-08-05 2020-07-31 Roue monocanal de pompe centrifuge fermée destinée à des fluides qui ont des mélanges abrasifs ou érosifs

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102019005469.5 2019-08-05
DE102019005469.5A DE102019005469A1 (de) 2019-08-05 2019-08-05 Geschlossenes Kreiselpumpenkanallaufrad für Flüssigkeiten mit abrasiven oder erosiven Beimengungen

Publications (1)

Publication Number Publication Date
WO2021023660A1 true WO2021023660A1 (fr) 2021-02-11

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PCT/EP2020/071669 WO2021023660A1 (fr) 2019-08-05 2020-07-31 Roue monocanal de pompe centrifuge fermée destinée à des fluides qui ont des mélanges abrasifs ou érosifs

Country Status (4)

Country Link
EP (1) EP4010598A1 (fr)
CN (1) CN114423951A (fr)
DE (1) DE102019005469A1 (fr)
WO (1) WO2021023660A1 (fr)

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20130336774A1 (en) * 2010-12-03 2013-12-19 Ihc Holland Ie B.V. Centrifugal pump and a double bent rotor blade for use in such a centrifugal pump
CN108331763A (zh) * 2018-02-27 2018-07-27 中交疏浚技术装备国家工程研究中心有限公司 一种提高使用寿命的耐用型泥泵的设计实现方法
US20180216627A1 (en) * 2014-08-26 2018-08-02 Ihc Holland Ie B.V. Impeller blade with asymmetric thickness
US20190120242A1 (en) * 2016-04-06 2019-04-25 Flsmidth A/S Low inlet vorticity impeller having enhanced hydrodynamic wear characteristics

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102015213451B4 (de) * 2015-07-17 2024-02-29 KSB SE & Co. KGaA Kreiselpumpen-Schaufelprofil

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20130336774A1 (en) * 2010-12-03 2013-12-19 Ihc Holland Ie B.V. Centrifugal pump and a double bent rotor blade for use in such a centrifugal pump
US20180216627A1 (en) * 2014-08-26 2018-08-02 Ihc Holland Ie B.V. Impeller blade with asymmetric thickness
US20190120242A1 (en) * 2016-04-06 2019-04-25 Flsmidth A/S Low inlet vorticity impeller having enhanced hydrodynamic wear characteristics
CN108331763A (zh) * 2018-02-27 2018-07-27 中交疏浚技术装备国家工程研究中心有限公司 一种提高使用寿命的耐用型泥泵的设计实现方法

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Publication number Publication date
DE102019005469A1 (de) 2021-02-11
CN114423951A (zh) 2022-04-29
EP4010598A1 (fr) 2022-06-15

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