EP0623752A1 - Rouet de pompe centrifuge - Google Patents

Rouet de pompe centrifuge Download PDF

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Publication number
EP0623752A1
EP0623752A1 EP94104842A EP94104842A EP0623752A1 EP 0623752 A1 EP0623752 A1 EP 0623752A1 EP 94104842 A EP94104842 A EP 94104842A EP 94104842 A EP94104842 A EP 94104842A EP 0623752 A1 EP0623752 A1 EP 0623752A1
Authority
EP
European Patent Office
Prior art keywords
blade
impeller
centrifugal pump
pump impeller
blades
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.)
Granted
Application number
EP94104842A
Other languages
German (de)
English (en)
Other versions
EP0623752B1 (fr
Inventor
Sönke Dr. Brodersen
Peter Hergt
Wolfgang Metzinger
Paul Krieger
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 AG
Original Assignee
KSB AG
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 AG filed Critical KSB AG
Publication of EP0623752A1 publication Critical patent/EP0623752A1/fr
Application granted granted Critical
Publication of EP0623752B1 publication Critical patent/EP0623752B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • 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
    • F04D29/2261—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
    • 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

Definitions

  • the invention relates to a centrifugal pump impeller for conveying liquids containing solids.
  • the invention is based on the problem of developing a measure which prolongs the service life of the pump for the centrifugal pump impellers used for the conveyance of liquids, in which hydroabrasive wear is to be expected.
  • An embodiment of the invention provides for this that the transitions of the blade beginnings from the impeller cover disks to the blades take the form of arcs or straight lines with gradients of 0 ° to a maximum of 30 °. Due to the flat rise provided in the area of the middle blade area or the flat transition from the impeller cover disks into the blade tips, a constant increase in speed is brought about in the area of the blade leading edge. This prevents the occurrence of a backflow and thus the formation of a swirl field, which can destroy the cover disks and the blade leading edges.
  • the flat transition in the plane of the middle blade surface from the cover disks into the blade tips can be carried out by material application and / or material removal.
  • material application and material removal used here are not used in a restrictive and objective manner, but describe the form of change of the invention compared to what is known up to now. In this sense, this also applies to cast, sprayed or similarly made impellers, in which a complete impeller is produced in one operation.
  • the impeller model or impeller shape which is then used already has the design which ensures the contours according to the invention.
  • the use of the terms material application or material removal refers to the general structural change of a previous blade or contour compared to the new one.
  • the measure comparable to material removal predominantly in the area of the impeller cover disk, enables the flat transition in the area of the middle blade area to the beginning of the blade.
  • the same effect can be achieved by the measure in the corners between the impeller cover disk and the beginning of the blade, which is comparable to a material application.
  • these measures should always be carried out in an extension of the middle blade area beyond the beginning of the blade.
  • the measures result in a new course of the blade starts on the impeller cover disk side. To a certain extent, the blade beginnings in the edge area on the impeller cover disc side are clearly drawn forward.
  • the configurations described in claims 3 to 5 indicate the orders of magnitude of the transitions or material removal.
  • the initial blade thickness is to be understood as the blade thickness that can be measured at the beginning of the blade according to the rounding radius between the suction and pressure sides of the blade. Practical tests have shown that if these values are switched on, the formation of vortices which damage the cover disks and the beginning of the blades can be prevented.
  • Another solution to the problem provides that in the area of the impeller inlet diameter and the impeller cover disk on the suction side, the blade tips protrude from the impeller with rounded blade tips.
  • the blade tip which usually protrudes in the area of the impeller cover disk on the suction side, has a rounded tip. This influences the flow before entering the impeller, and the formation of a vortex field within the impeller and in front of the beginning of the blade can be effectively prevented.
  • the centrifugal pump shown in Fig. 1 for conveying media containing solids is of a single-stage design.
  • An impeller 2 is shown within a housing 1, the blades 3 of which are shown in the meridian section and projected into the sectional plane are arranged between the suction-side impeller cover plate 4 and the pressure-side impeller cover plate 5.
  • the latter is also known under the term support disc.
  • the blade tips 6 extend between the two cover disks.
  • the inlet cross section of the impeller is limited by the impeller end face 2.1.
  • Fig. 2 shows a flat development of a blade, the section of which runs through the middle blade surface.
  • material accumulations 8, 9 of the blade 3 are preceded. Seen in the direction of flow, the transition from the impeller cover disks 4, 5 into the material accumulations 8, 9 acting as an advanced blade leading edge occurs at a very flat angle ⁇ in this plane.
  • the radius of this arc is equal to or greater than that 2.5 times the initial blade thickness D.
  • the initial blade thickness D is predominantly constant here, but can initially rise over a short distance in the initial area, which is shown as a circular arc in FIGS. 3 and 4, for other contours, such as ellipses.
  • Decisive for the transition radius R shown in FIG. 2 from the impeller cover plate to the beginning of the blade 6 is the blade thickness which can be measured at the beginning of the blade; 3 and 4, therefore, the diameter of the semicircle at the character I. This applies if the blade surfaces are arranged perpendicular to the cover disks.
  • the blade surfaces are arranged inclined at an angle to the cover disks, then the blade thickness D that results from a cut running parallel to the impeller cover disk surface is decisive.
  • the radius R which has a flat increase, also increases.
  • FIG. 3 shows a top view of the blade 3 of FIG. 2 cut according to the lines I-I to IV-IV.
  • This is a blade with a small transition radius between the blade and the cover plate in the area of the blade channels.
  • the lines marked in this illustration with the characters I to IV are comparable in their function with contour lines.
  • the dash-dotted line 11 corresponds to the plane of the middle blade surface, the blade thickness of the blade tips 6 was marked with D.
  • FIG. 4 shows an embodiment in which the blade 3 merges directly into the cover plate without a radius of rounding.
  • FIG 5 shows an embodiment in which a flat transition 13 in the plane of the middle blade surface to the blade tips 6 takes place both by a material removal 12 in the area of the cover disks 4, 5 and by a material application 8, 9 at the blade tips 6 .
  • the section lines I to IV shown here run parallel to the cover plate. This course of the cutting line results in a blade contour corresponding to a height profile, as was shown in FIGS. 3 and 4.
  • the material removal 12 carried out on the cover disks should be at least twice greater than the initial blade thickness D. In this illustration, the material removal 12 extends into the blade channel. With an appropriate design of the blade transition to the cover plate, the expansion can also end before the blade starts and leave the blade channels unaffected.
  • FIG. 6 shows a blade tip (14) which is drawn forward beyond the impeller end face 2.1 in the area of the suction-side impeller cover disk 4. In the area of the impeller cover disk 5 on the pressure side, the flat rise into the blade tips 6 already discussed above is shown.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Geometry (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
EP94104842A 1993-04-08 1994-03-28 Rouet de pompe centrifuge Expired - Lifetime EP0623752B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4311746A DE4311746A1 (de) 1993-04-08 1993-04-08 Kreiselpumpenlaufrad
DE4311746 1993-04-08

Publications (2)

Publication Number Publication Date
EP0623752A1 true EP0623752A1 (fr) 1994-11-09
EP0623752B1 EP0623752B1 (fr) 1998-09-09

Family

ID=6485168

Family Applications (1)

Application Number Title Priority Date Filing Date
EP94104842A Expired - Lifetime EP0623752B1 (fr) 1993-04-08 1994-03-28 Rouet de pompe centrifuge

Country Status (3)

Country Link
US (1) US5478200A (fr)
EP (1) EP0623752B1 (fr)
DE (2) DE4311746A1 (fr)

Families Citing this family (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0988887A (ja) * 1995-09-20 1997-03-31 Unisia Jecs Corp ウォータポンプ
US6435829B1 (en) 2000-02-03 2002-08-20 The Boeing Company High suction performance and low cost inducer design blade geometry
US6589015B1 (en) 2002-05-08 2003-07-08 Pratt & Whitney Canada Corp. Discrete passage diffuser
JP4663259B2 (ja) * 2004-06-18 2011-04-06 日立アプライアンス株式会社 送風機及び電気掃除機
CN102369356B (zh) 2008-09-10 2014-11-19 滨特尔泵集团股份有限公司 高效、多级离心泵及其装配方法
US8235648B2 (en) * 2008-09-26 2012-08-07 Pratt & Whitney Canada Corp. Diffuser with enhanced surge margin
JP5164932B2 (ja) * 2009-06-11 2013-03-21 三菱電機株式会社 ターボファンおよび空気調和機
EP2486283B1 (fr) * 2009-10-08 2018-12-05 Sulzer Management AG Roue de pompe
US8998582B2 (en) 2010-11-15 2015-04-07 Sundyne, Llc Flow vector control for high speed centrifugal pumps
CN106337833A (zh) 2015-07-06 2017-01-18 杭州三花研究院有限公司 叶轮、离心泵以及电驱动泵
US9926942B2 (en) 2015-10-27 2018-03-27 Pratt & Whitney Canada Corp. Diffuser pipe with vortex generators
US10570925B2 (en) 2015-10-27 2020-02-25 Pratt & Whitney Canada Corp. Diffuser pipe with splitter vane
WO2017175165A1 (fr) * 2016-04-06 2017-10-12 Flsmidth A/S Roue à faible vorticité d'entrée ayant des caractéristiques d'usure hydrodynamique améliorées
WO2018049435A1 (fr) * 2016-09-08 2018-03-15 Mechanical Engineering Transcendent Technology (Pty) Ltd Profil d'aube primaire de turbine
US10823197B2 (en) 2016-12-20 2020-11-03 Pratt & Whitney Canada Corp. Vane diffuser and method for controlling a compressor having same
NL2018044B1 (en) * 2016-12-22 2018-06-29 Ihc Holland Ie Bv Impeller with rotor blades for centrifugal pump
US11959487B2 (en) * 2020-09-30 2024-04-16 Weir Slurry Group, Inc. Centrifugal slurry pump impeller

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1946273A (en) * 1932-02-08 1934-02-06 American Manganese Steel Co Rotary pump impeller
US3130678A (en) * 1961-04-28 1964-04-28 William F Chenault Centrifugal pump
SU1101590A1 (ru) * 1983-02-17 1984-07-07 Специальное Конструкторско-Технологическое Бюро Герметичных И Скважинных Насосов Рабочее колесо центробежного насоса
GB2256901A (en) * 1991-06-21 1992-12-23 Ingersoll Rand Co Impeller for centrifugal pumps.

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1246253A (en) * 1916-10-31 1917-11-13 Alexander T Fraser Pump.
US1947658A (en) * 1931-12-17 1934-02-20 Pizzuto Nicolas Impeller and shaft therefor for use in centrifugal and turbine pumps
US2625884A (en) * 1949-02-23 1953-01-20 William H Welsh Impeller
CH294450A (de) * 1952-12-10 1953-11-15 Schweizer Becker Werner Zentrifugalpumpe, insbesondere für dickflüssige Medien.
US3260443A (en) * 1964-01-13 1966-07-12 R W Kimbell Blower
US3272429A (en) * 1964-10-16 1966-09-13 Westinghouse Electric Corp Rotors of centrifugal fans
DE2532791A1 (de) * 1975-07-22 1977-02-10 Dessair Jean Paul Vertikal- oder horizontaltraeger fuer die herstellung und einrichtung von bueroraeumen sowie haupt- und hilfsprofile zum zusammenbau eines solchen traegers
DD253279A1 (de) * 1986-10-09 1988-01-13 Pumpen & Verdichter Veb K Pumpenlaufrad fuer die foerderung von fluessigkeits-feststoff-gemischen
DE3704360A1 (de) * 1987-02-12 1988-08-25 Klein Schanzlin & Becker Ag Kreiselpumpe zur foerderung von feststoffhaltigen fluessigkeiten

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1946273A (en) * 1932-02-08 1934-02-06 American Manganese Steel Co Rotary pump impeller
US3130678A (en) * 1961-04-28 1964-04-28 William F Chenault Centrifugal pump
SU1101590A1 (ru) * 1983-02-17 1984-07-07 Специальное Конструкторско-Технологическое Бюро Герметичных И Скважинных Насосов Рабочее колесо центробежного насоса
GB2256901A (en) * 1991-06-21 1992-12-23 Ingersoll Rand Co Impeller for centrifugal pumps.

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
SOVIET PATENTS ABSTRACTS Section PQ Week 8507, 27 March 1985 Derwent World Patents Index; Class Q56, AN 85-043087 *

Also Published As

Publication number Publication date
US5478200A (en) 1995-12-26
EP0623752B1 (fr) 1998-09-09
DE59406861D1 (de) 1998-10-15
DE4311746A1 (de) 1994-10-13

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