EP2148096B1 - Pompe centrifuge - Google Patents

Pompe centrifuge Download PDF

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Publication number
EP2148096B1
EP2148096B1 EP08013390.3A EP08013390A EP2148096B1 EP 2148096 B1 EP2148096 B1 EP 2148096B1 EP 08013390 A EP08013390 A EP 08013390A EP 2148096 B1 EP2148096 B1 EP 2148096B1
Authority
EP
European Patent Office
Prior art keywords
seal
impeller
centrifugal pump
pump according
fastening ring
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.)
Not-in-force
Application number
EP08013390.3A
Other languages
German (de)
English (en)
Other versions
EP2148096A1 (fr
Inventor
Jørgen Schmidt
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.)
Grundfos Management AS
Original Assignee
Grundfos Management AS
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 Grundfos Management AS filed Critical Grundfos Management AS
Priority to EP08013390.3A priority Critical patent/EP2148096B1/fr
Priority to CN2009801292004A priority patent/CN102105696B/zh
Priority to PCT/EP2009/004688 priority patent/WO2010009799A1/fr
Priority to US13/054,585 priority patent/US8721263B2/en
Publication of EP2148096A1 publication Critical patent/EP2148096A1/fr
Application granted granted Critical
Publication of EP2148096B1 publication Critical patent/EP2148096B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F04D29/08—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

Definitions

  • Centrifugal pumps have a gap between the rotating impeller and the stationary pump member surrounding the impeller. In order to reduce leakage losses occurring at the gap from the impeller pressure side to the impeller suction side, gap seals are provided.
  • gap seals are made US 2006/0147328 A1 and US 2007/0160467 A1 known.
  • the gap seals described therein are mounted on a stationary pump part which separates the impeller pressure side from the impeller suction side.
  • the width of this gap can be designed so that no appreciable loss of leakage can occur, but then there is a risk of friction between the impeller and the gap seal, which can lead to wear of the friction partners involved and particularly unfavorable to a blocked pump.
  • the dilemma is to have to accept a relatively high wear and a blockage of the pump or otherwise with a larger gap, although a lower wear but relatively large leakage losses either at a narrow, low leakage causing gap.
  • the invention has for its object to provide a centrifugal pump with a gap seal, which should be further improved in the wear characteristics at the lowest possible leakage from the impeller pressure side to the impeller suction.
  • the centrifugal pump according to the invention has at least one impeller and at least one sealing arrangement which is arranged between a housing wall of the pump housing and the impeller and thus seals the suction side of the impeller against the pressure side of the impeller.
  • the seal assembly has a seal which is rotatably attached to the impeller.
  • the seal On the impeller, the seal is slidably disposed in the radial direction relative to the impeller. Particularly advantageously, the seal is mounted on the impeller so that it can move radially in any direction transverse to a central axis of the impeller substantially. This allows a narrow formation of the required gap between the seal rotating with the impeller and the fixed part of the seal assembly, since the seal is e.g. then, when a foreign body has penetrated into the gap or when the seal contacts the fixed part of the seal assembly due to a deflection of the impeller shaft, can perform a short-time increasing evasion movement of the gap.
  • the radial distance of the seal from the fixed part of the seal assembly at the location where it contacts the fixed part or at which a foreign body is located be increased so that it is favorable no abrasive wear on the seal and / or the fixed part of the seal assembly comes.
  • the invention further provides, in a further advantageous embodiment, for the seal to be designed to be flexible at least in sections.
  • the seal preferably has elastic deformability, and preferably elastic flexibility, at least in a portion adjacent to the gap with the fixed part of the seal assembly. These are preferably a deformability transversely to its sealing surface with the fixed part of the seal assembly. This elasticity also allows a deflection movement of the seal in a deflection of the impeller shaft or in a foreign body penetrated into the seal assembly.
  • the seal is designed as an axial seal, wherein for the purposes of the invention an axial seal is to be understood as meaning a seal in which the seal takes place in the axial direction of the impeller, ie the sealing surfaces extend in the axial direction of the impeller.
  • An embodiment is preferred in which the seal is arranged on a suction mouth of the impeller, wherein it has a hollow cylindrical portion which extends in the axial direction of the impeller.
  • the suction mouth of the impeller is typically formed centrally on a front cover plate in the inflow direction of the impeller.
  • the seal is preferably mounted in such a way that the inner wall of the hollow cylindrical section, which preferably forms a sealing surface of the seal arrangement, is aligned substantially flush with the edge of the suction mouth.
  • a sleeve-shaped stationary part of the seal arrangement which is expediently arranged on the housing of the centrifugal pump or on the housing wall, engage in the hollow cylindrical portion of the seal.
  • the outer cross-section or outer diameter of the sleeve-shaped part of the seal assembly, which engages in the hollow cylindrical portion of the impeller-side arranged seal expediently corresponds to the inner cross-section or inner diameter of the hollow cylindrical portion of the seal, wherein a formed between the sleeve-shaped part and the hollow cylindrical portion of the seal gap may advantageously be relatively narrow. Accordingly, only relatively small leaks can occur at the gap. In view of these leaks, it also proves to be advantageous that the gap at least in one end portion extends in the inflow direction of the sucked by the pump liquid and is open to the hem and out, so that the resulting leakage liquid can be sucked directly on the suction mouth.
  • a particularly small gap width can be achieved if the impeller-side seal, as already described, at least partially flexible and / or this seal is displaceable in the radial direction relative to the impeller.
  • These embodiments cause the impeller-side seal in the case of friction with the housing-side sleeve-shaped part of the seal assembly can escape this sleeve-shaped part in the radial direction, i. can move radially away from this part.
  • the housing-side part of the seal assembly and the seal can align themselves so independently.
  • the ability of the impeller-side seal to be able to move in the radial direction of the impeller relative to the impeller also proves to be advantageous insofar as by such a displacement of the impeller-side seal, similar to a hydrodynamic sliding bearing, a narrowing in the radial direction gap between the impeller side and the housing side seal results.
  • This wedge-shaped gap leads to a hydrodynamic pressure distribution in the gap, whereby a force is exerted on the radially movable impeller-side seal, which tends to move the hollow cylindrical portion of the seal again in a concentric position to the housing-side sleeve-shaped part of the seal assembly.
  • the gasket is capable of returning to its normal position on its own.
  • the seal may be attached to the impeller advantageously with a preferably flexible mounting ring.
  • a section of the impeller preferably an axial end of the impeller surrounding the suction mouth, and a section of the seal which contacts this section or end have an at least substantially corresponding external cross section.
  • the flexibility of the mounting ring makes it possible in this case advantageous that the mounting ring can be placed under strain in a simple manner around the contacting portions of the impeller and the seal and then exerts a clamping force on these sections, whereby the seal positively and / or non-positively on the Impeller is set.
  • the seal to attach the seal to the impeller preferably has both an end of the seal and an axial end of the impeller on a radially outwardly cantilevered flange extension, wherein the two extensions for fixing together engage in an inner groove of the extension ring attached to the attachment.
  • the seal is positively fixed not only in the radial direction but also in the axial direction of the mounting ring.
  • the attachment ring preferably holds the seal with radial play on the impeller.
  • the attachment ring may comprise an extension formed at the end of the seal, the extension having a small clearance in the radial direction to the attachment ring, which advantageously permits limited deflection movements of the sealing ring in the radial direction relative to the rotor.
  • the seal is rotatably connected via a positive connection with the impeller.
  • This positive connection can be generated either directly between the seal and the impeller or on the mounting ring by the intervention of at least one engagement means in at least one corresponding receptacle for this engagement means, which is basically arbitrary, on which component or on which components Engagement means and on which component or which components receptacles are provided for these engagement means.
  • a preferred embodiment provides that at least one engagement means is formed on a suction mouth side facing the seal, which is in engagement with a corresponding engagement means on the impeller. That is, the positive connection is made here directly between the seal and the impeller.
  • recesses may be formed on an annular end surface of the gasket contacting the impeller, while corresponding protrusions are formed on an impeller side contact surface which engage with the gasket side recesses and fix the gasket against rotation relative to the impeller, preferably maintaining a certain radial mobility remains.
  • the projections are provided on the sealing side and the recesses on the impeller side.
  • the fastening ring may also be advantageous to form in the inner groove of the fastening ring at least one radially oriented projection, which engages in a corresponding radial recess of suction mouth and / or seal.
  • the mounting ring is made of an elastic material, such as rubber, since in the torque transmission from the impeller to the seal may possibly shocks from the impeller on the seal may occur, the noise caused thereby by the elastic material of the Mounting ring are damped.
  • the centrifugal pump it is provided to non-rotatably connect the seal to the suction mouth by virtue of frictional engagement.
  • the impeller-side and the sealing-side contact surface and possibly also a fixing ring serving for fastening the seal to the impeller can each be designed to form a frictional connection.
  • the seal and the fastening ring can be advantageously formed as an integral component.
  • an annular portion is provided at an axial end of the seal, which includes an axial end of the impeller circumferentially.
  • the portion forming the seal and the portion of the component forming the fastening ring are in this case made of an elastic material.
  • an impeller 4 driven by an impeller 2 of a centrifugal pump is shown in each case.
  • a suction port 10 is formed at one axial end 8.
  • a seal 12 is arranged.
  • the seal 12 is formed of an elastic material, preferably rubber. It has a hollow cylindrical portion 14 in the form of a base body 14, which is aligned axially and concentrically to a central axis A of the impeller 4.
  • the main body 14 forms an inflow channel to the suction mouth 10 of the impeller. 4
  • a rigid, sleeve-shaped portion 16 of a sealing member 18 At the end remote from the impeller 4 of the base body 14 engages a rigid, sleeve-shaped portion 16 of a sealing member 18 with a small clearance, ie, forming a comparatively narrow Gaps, in the main body 14 a.
  • the sealing member 18 is fixedly arranged on a housing wall, not shown in the figures of a pump housing also not shown and forms an inlet to the suction port 10 of the impeller 4.
  • the impeller-side seal 12 and the sleeve-shaped portion 16 of the housing wall sealing member 18 form a seal assembly, the the suction side of the impeller 4 seals against the pressure side of the impeller 4.
  • the gap between the main body 14 of the seal 12 and the housing wall sealing member 18 can flow only a small amount of liquid from the pressure side of the impeller 4 to the suction side, wherein it proves to be particularly advantageous that the gap between the base body 14 and the sleeve-shaped portion 16 of the sealing member 18 concentric with the central axis A of the impeller 4 extends directly in the direction of the suction mouth 10 of the impeller 4, so that the leaked liquid can be sucked in again by the impeller 4 again.
  • the axial end 8 of the impeller 4 to the suction port 10 is formed in a flange, wherein a, a contact surface for the seal 14 forming end portion is radially expanded.
  • the end of the seal 8, which is to be brought to bear on the end 8 of the impeller 4, is also expanded in the radial direction, the inner and outer diameter of this extension 21 corresponding to the corresponding diameters of the extension 19 formed at the end 8.
  • the mounting ring 20 is made of elastic material, preferably rubber.
  • the fixing ring 20 is circumferentially so placed around the end 8 of the impeller 4 and the seal 12 that the formed at the end of the extension 19th and formed on the seal 12 extension 21 engage together in the groove 22 of the mounting ring 20 so that the mounting ring 20 includes these extensions 19 and 21 both axially and radially, wherein in the radial direction between the seal-side extension 21 and the circumferential inner wall of the Nut 22 is a small game. If necessary, this play allows a deflection movement of the seal 12 relative to the sleeve-shaped section 16 of the sealing part 18 transversely to the central axis A of the running wheel 4.
  • the seal 12 is fixed by the mounting ring 22 in both the radial and in the axial direction at the end 8 of the impeller 4.
  • six projections 24 are formed on the outer end face of the end 8 of the impeller 4 evenly distributed over the circumference of this end face extending in the axial direction.
  • six recesses 26 are formed at the front end of the seal 12 formed on the extension 21, in which the projections 24 engage positively.
  • recesses 28 and 30 are on the inner circumference of the groove 22 of the mounting ring 20 evenly distributed over the inner circumference six projections 32 are formed.
  • the projections 32 extend radially inwardly. In the assembled state, the projections 32 of the mounting ring 20 positively engage both in the recesses 28 of the extension 19 as in the recesses 30 of the extension 21 and thus prevent a rotational movement of the seal 12 relative to the impeller. 4
  • projections 19 or 21 projections or recesses are formed neither on the front side nor on the peripheral side of the extensions.
  • the rotationally fixed arrangement of the seal 12 at the end 8 of the impeller 4 by means of adhesion for this purpose, the end and peripheral surfaces of the extensions 19 and 21 as well as the side contacting the region of the groove 22 of the mounting ring 20 form a friction pair, which prevents rotation of the seal 12 relative to the impeller 4.
  • seal 12 at the end 8 of the impeller 4 rotatably fixed by frictional engagement.
  • a seal 12 ' is provided, in which a hollow cylindrical body 14' and a mounting ring 20 'form an integral component, that are firmly connected to each other.

Landscapes

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

Claims (13)

  1. Pompe centrifuge comprenant au moins un rotor (4) et au moins un dispositif d'étanchéité interposé entre le rotor (4) et une paroi de corps, qui isole hermétiquement le côté aspiration du rotor (4) du côté pression du rotor (4) et qui présente une garniture d'étanchéité (12) fixée solidairement en rotation au rotor (4), caractérisée en ce que la garniture d'étanchéité (12) est mobile dans la direction radiale par rapport au rotor (4).
  2. Pompe centrifuge selon l'une des revendications précédentes, caractérisée en ce que la garniture d'étanchéité (12) est de constitution flexible, au moins par segments.
  3. Pompe centrifuge selon l'une des revendications précédentes, caractérisée en ce que la garniture d'étanchéité (12) est disposée au niveau d'une bouche d'aspiration (10) du rotor (4) et présente un segment cylindrique creux (14) qui s'étend dans la direction axiale.
  4. Pompe centrifuge selon la revendication 3, caractérisée en ce qu'une partie fixe (16) en forme de manchon du dispositif d'étanchéité est engagée dans le segment cylindrique creux (14) de la garniture d'étanchéité (12).
  5. Pompe centrifuge selon l'une des revendications précédentes, caractérisée en ce que la garniture d'étanchéité (12) est fixée au rotor (4) au moyen d'une bague de fixation (20).
  6. Pompe centrifuge selon la revendication 5, caractérisée en ce que la bague de fixation est de constitution flexible.
  7. Pompe centrifuge selon la revendication 6, caractérisée en ce que tant une extrémité de la garniture d'étanchéité (12) que l'extrémité (8) de la bouche d'aspiration (10) présentent un agrandissement (19, 21) en forme de collerette en saillie vers l'extérieur, lesquels agrandissements s'engagent ensemble dans une gorge intérieure (22) de la bague de fixation (20) disposée autour des agrandissements (19, 21) pour assurer la fixation.
  8. Pompe centrifuge selon l'une des revendications 6 ou 7, caractérisée en ce que la bague de fixation (20) maintient la garniture d'étanchéité (12) assemblée au rotor (4) avec un jeu radial.
  9. Pompe centrifuge selon l'une des revendications précédentes, caractérisée en ce que la garniture d'étanchéité (12) est assemblée solidairement en rotation au rotor (4) par engagement mécanique.
  10. Pompe centrifuge selon la revendication 9, caractérisée en ce que, sur un côté de la garniture d'étanchéité (12) qui est dirigé vers la bouche d'aspiration (10) est formé au moins un moyen de prise qui est en prise avec un moyen de prise correspondant porté par le rotor (4).
  11. Pompe centrifuge selon la revendication 9, caractérisée en ce que, dans la gorge intérieure (22) de la bague de fixation (20), est formée au moins une saillie (32) orientée radialement, qui s'engage dans des évidements radiaux correspondants (28, 30) de la bouche d'aspiration (10) et/ou de la garniture d'étanchéité (12).
  12. Pompe centrifuge selon l'une des revendications 1 à 7, caractérisée en ce que la garniture d'étanchéité (12) est assemblée solidairement en rotation à la bouche d'aspiration (10) par adhérence.
  13. Pompe centrifuge selon l'une des revendications précédentes, caractérisée en ce que la garniture d'étanchéité (12) et la bague de fixation (20) constituent une pièce monobloc.
EP08013390.3A 2008-07-25 2008-07-25 Pompe centrifuge Not-in-force EP2148096B1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
EP08013390.3A EP2148096B1 (fr) 2008-07-25 2008-07-25 Pompe centrifuge
CN2009801292004A CN102105696B (zh) 2008-07-25 2009-06-30 离心泵
PCT/EP2009/004688 WO2010009799A1 (fr) 2008-07-25 2009-06-30 Pompe centrifuge
US13/054,585 US8721263B2 (en) 2008-07-25 2009-06-30 Centrifugal pump

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP08013390.3A EP2148096B1 (fr) 2008-07-25 2008-07-25 Pompe centrifuge

Publications (2)

Publication Number Publication Date
EP2148096A1 EP2148096A1 (fr) 2010-01-27
EP2148096B1 true EP2148096B1 (fr) 2013-04-10

Family

ID=40019309

Family Applications (1)

Application Number Title Priority Date Filing Date
EP08013390.3A Not-in-force EP2148096B1 (fr) 2008-07-25 2008-07-25 Pompe centrifuge

Country Status (4)

Country Link
US (1) US8721263B2 (fr)
EP (1) EP2148096B1 (fr)
CN (1) CN102105696B (fr)
WO (1) WO2010009799A1 (fr)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102010026450B3 (de) * 2010-07-08 2011-12-01 Ksb Aktiengesellschaft Kreiselpumpenbauteil
DE102010063108A1 (de) 2010-12-15 2012-06-21 Ksb Aktiengesellschaft Dichtungsanordnung für Kreiselpumpen
EP2607710B1 (fr) * 2011-12-23 2015-04-08 Grundfos Holding A/S Pompe centrifuge de type humide
US9739284B2 (en) * 2013-11-19 2017-08-22 Charles Wayne Zimmerman Two piece impeller centrifugal pump
EP3339654B1 (fr) * 2016-12-20 2021-03-03 Grundfos Holding A/S Pompe centrifuge
CN108331782A (zh) * 2018-01-29 2018-07-27 陈恒平 一种离心泵闭式叶轮

Family Cites Families (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2109679A (en) * 1936-04-13 1938-03-01 Sr Aloys Neveling Sealing device for pumps
US2140644A (en) * 1937-05-24 1938-12-20 Ingersoll Rand Co Locking device
US2250311A (en) * 1938-03-16 1941-07-22 Rotary Seal Company Seal
US2452253A (en) * 1945-01-29 1948-10-26 Daniel F Mcgill Floating sealing device
GB730459A (en) * 1953-10-16 1955-05-25 Hathaway Ltd L High pressure pumping unit for fire-fighting purposes
US3020850A (en) * 1958-02-27 1962-02-13 Meckum Engineering Inc Dredge pump seal
BE767910A (fr) * 1971-06-01 1971-11-03 Rheinstahl Giesserei Ag Pompe radiale resistant a l'usure et destinee au debit de melanges liquides/matieres solides.
IT209616Z2 (it) * 1986-08-08 1988-10-24 Lowara Spa Anello di tenuta idraulica sulla bocca della girante in pompe mono e pluristadio.
CN2035013U (zh) * 1988-04-07 1989-03-29 湘潭市食品机械总厂 饮料泵自动调整端面密封装置
DE50012259D1 (de) * 2000-01-11 2006-04-27 Sulzer Pumpen Ag Winterthur Strömungsmaschine für ein Fluid mit einem radialen Dichtspalt zwischen Statorteilen und einem Rotor
EP1116886B1 (fr) * 2000-01-11 2006-02-22 Sulzer Pumpen Ag Machine rotative pour fluide à jeu d'étanchéité radial entre les parties du stator et un rotor
US6679678B2 (en) * 2002-05-31 2004-01-20 Honeywell International, Inc. Increased wear-life mechanical face seal anti-rotation system
US6921245B2 (en) * 2003-02-11 2005-07-26 Envirotech Pumpsystems, Inc. Coaxial seal for a pump
JP4532142B2 (ja) 2003-12-22 2010-08-25 株式会社荏原製作所 流体機械のシール機構又は遠心ポンプ
DE502006004968D1 (de) 2006-01-12 2009-11-12 Sulzer Pumpen Ag Strömungsmaschine für ein Fluid mit einem radialen Dichtspalt

Also Published As

Publication number Publication date
US20110123317A1 (en) 2011-05-26
WO2010009799A1 (fr) 2010-01-28
EP2148096A1 (fr) 2010-01-27
CN102105696B (zh) 2013-08-07
US8721263B2 (en) 2014-05-13
CN102105696A (zh) 2011-06-22

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