EP2706238B1 - Pompe centrifuge comprenant une protection de roue mobile avec une gorge annulaire et un joint radial - Google Patents

Pompe centrifuge comprenant une protection de roue mobile avec une gorge annulaire et un joint radial Download PDF

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Publication number
EP2706238B1
EP2706238B1 EP13180050.0A EP13180050A EP2706238B1 EP 2706238 B1 EP2706238 B1 EP 2706238B1 EP 13180050 A EP13180050 A EP 13180050A EP 2706238 B1 EP2706238 B1 EP 2706238B1
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EP
European Patent Office
Prior art keywords
impeller
protector
pump housing
impeller protector
centrifugal pump
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.)
Active
Application number
EP13180050.0A
Other languages
German (de)
English (en)
Other versions
EP2706238A2 (fr
EP2706238A3 (fr
Inventor
Sascha Korupp
Lars Runte
Felix Hees
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.)
Herborner Pumpentechnik & Co KG GmbH
Original Assignee
Herborner Pumpentechnik & Co KG GmbH
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 Herborner Pumpentechnik & Co KG GmbH filed Critical Herborner Pumpentechnik & Co KG GmbH
Priority to PL13180050T priority Critical patent/PL2706238T3/pl
Publication of EP2706238A2 publication Critical patent/EP2706238A2/fr
Publication of EP2706238A3 publication Critical patent/EP2706238A3/fr
Application granted granted Critical
Publication of EP2706238B1 publication Critical patent/EP2706238B1/fr
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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
    • F04D29/40—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
    • F04D29/4286—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for liquid pumps inside lining, e.g. rubber
    • 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
    • F04D29/02—Selection of particular materials
    • F04D29/026—Selection of particular materials especially adapted for liquid 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
    • 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
    • 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
    • F05D2260/00—Function
    • F05D2260/95—Preventing corrosion
    • 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
    • F05D2300/00—Materials; Properties thereof
    • F05D2300/40—Organic materials
    • F05D2300/43—Synthetic polymers, e.g. plastics; Rubber
    • 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
    • F05D2300/00—Materials; Properties thereof
    • F05D2300/40—Organic materials
    • F05D2300/43—Synthetic polymers, e.g. plastics; Rubber
    • F05D2300/432—PTFE [PolyTetraFluorEthylene]

Definitions

  • the invention relates to a centrifugal pump according to claim 1.
  • Centrifugal pumps are used to pump pump media, which are usually liquids.
  • the pump medium enters the centrifugal pump through the inlet and is conveyed to the pressure side by rotating the impeller and discharged under pressure through the outlet.
  • the outlet is often located radially with respect to the impeller, a radial flow being generated by the impeller.
  • Adequate sealing is required between the pressure side and the suction side for good pump efficiency.
  • the impeller interacts with an impeller seat that is stationary in the pump housing. To move the impeller relatively To enable the impeller seat, the most complete possible seal between the impeller and impeller seat requires a precisely fitting production and, if necessary, additional sealing. This makes the production of the pump complex and expensive.
  • centrifugal pumps Due to unavoidable manufacturing tolerances, centrifugal pumps often hear unpleasant grinding noises when they are started up, which stop only after a certain running-in period. These grinding noises result from contact between the impeller and the impeller seat and cause material to be removed from at least one of these two elements. However, this also creates bypass connections, i.e. leaks, between the suction side and the pressure side. Replacing the impeller is also relatively problematic, since the new impeller will then generally not match the shape of the old impeller seat.
  • the invention is based on the object of eliminating the disadvantages of the prior art and, in particular, of specifying a solution with which the service life of a centrifugal pump can be extended and which is particularly easy to maintain, offer play compensation and improves the efficiency of the centrifugal pump.
  • the impeller seat in an annular impeller protector made of a corrosion-resistant material which is accommodated in the pump housing, an insertion region of the impeller being radially surrounded by the impeller protector.
  • a radial seal is arranged between the impeller protector and the pump housing, the radial seal having a sealing lip that is inclined with respect to an axial direction and rests with a suction-side surface on the pump housing or on the impeller protector.
  • an annular groove is formed in a peripheral surface of the impeller protector, in which the radial seal is held.
  • the impeller seat which seals the pressure side of the pump from a suction side through interaction with the impeller, is therefore not, as was customary in the prior art, integrally formed in the pump housing and / or inserted as an additional component here in a fixed connection, but in one additional dynamic element, the wheel protector.
  • the impeller protector can be manufactured with little effort with a relatively high accuracy of fit, so that dynamic play compensation between the impeller protector and the pump housing takes place. This allows a gap between the impeller seat and the impeller to be kept very small, so that a high degree of efficiency can be achieved.
  • the impeller is guided radially and axially in the impeller protector.
  • the position of the impeller is therefore specified very precisely by the impeller protector.
  • the impeller protector can have a radially inwardly projecting collar which serves as an axial stop for the impeller and forms part of the impeller seat. This results in a very long sealing gap and thus a good seal.
  • the impeller protector bears with an end face against a stop of the pump housing.
  • the stop can be designed, for example, as a radially circumferential, radially inwardly projecting web of the pump housing, against which the impeller protector bears.
  • the axial position of the impeller protector within the pump housing is clearly defined. A first seal between the pump housing and the impeller protector is already obtained by the impeller protector against the stop. This prevents the impeller protector from being bypassed by the pump medium.
  • the end face of the impeller protector is preferably bevelled or rounded at least on a radial outer edge. This makes it easier to insert the impeller protector into the pump housing. In addition, there are manufacturing advantages in which between geometric overdetermination is avoided for the pump housing and the impeller protector.
  • the impeller protector has a plastic material, in particular POM or PTFE.
  • Thermoplastic materials are particularly suitable as the plastic material.
  • Such plastics have high thermal stability and absolute resistance to corrosion.
  • plastics have a lower water absorption and are easy to process.
  • POM and PTFE are also characterized by high strength, sufficient hardness and rigidity, high abrasion resistance and a low coefficient of friction.
  • a sliding pairing can then be formed between the impeller and the impeller seat or the impeller protector, in which the impeller slides on the impeller seat or an inside of the impeller protector. Due to the material of the impeller protector, only slight friction losses occur, which only play a subordinate role in view of the achievable advantages due to the good seal between the impeller seat and the impeller. Overall, a centrifugal pump with very high efficiency is obtained.
  • a radial seal is arranged between the impeller protector and the pump housing for sealing and dynamic movement compensation between the impeller protector and the pump housing.
  • the radial seal is usually designed as a ring seal and prevents a bypass connection or leakage between the impeller protector and the pump housing, even if the impeller protector has radial play, that is to say is movable with respect to the pump housing.
  • the radial seal has a sealing lip which is inclined with respect to an axial direction and which bears with a suction-side surface on the pump housing or on the impeller protector.
  • This sealing lip for example a "Viton rubber lip"
  • the inclined design of the sealing lip ensures that the sealing lip is pressed against the pump housing or the impeller protector by the pressure of the pump medium on the pressure side, so that the sealing effect of the seal is simultaneously improved with increasing pressure.
  • a radial gap between the pump housing and the impeller protector which is favorable, for example, to compensate for play, can then easily be covered by the radial seal with the sealing lip, so that an adequate Centering between the impeller and the pump housing or the impeller protector is made possible.
  • the radial seal is held in an annular groove which is formed in a peripheral surface of the impeller protector.
  • Such an annular groove is relatively easy to produce and ensures, for example, that the radial seal is in a defined position when the impeller protector is inserted into the pump housing. This simplifies the assembly of the centrifugal pump.
  • a groove opening of the annular groove is preferably smaller than a groove base, the annular groove in particular having side flanks which are inclined towards one another.
  • the radial seal is preferably preloaded between the impeller protector and the pump housing.
  • the radial preload can be generated, for example, by deforming the sealing lip.
  • the preload can be used to generate a non-positive hold of the impeller protector in the pump housing.
  • the preload of the radial seal ensures a sufficient seal even if the impeller protector is slightly offset from the pump housing to compensate for play. A radial air gap between the pump housing and the impeller protector is therefore reliably sealed by the radial seal.
  • FIG. 1 a centrifugal pump 1 with a multi-part pump housing 2 is shown.
  • the pump housing 2 has an inlet 3 and a radial outlet 4.
  • an insertion area 7 of the impeller 5 extends into an annular impeller protector 8.
  • the impeller protector 8 has a radially inwardly directed, circumferential collar 9 and forms an impeller seat 10 for the impeller 5.
  • the impeller 5 is for this purpose on the impeller seat 10 or Inner surfaces of the impeller protector 8 are slidably guided so that the pump medium, such as swimming pool water, which is conveyed from the inlet 3 to the outlet 4, cannot flow between the impeller protector 8 and the impeller 5, but is carried radially by the impeller 5 and so in a pressure channel 11 and from there to the outlet 4.
  • the impeller 8 provides radial and axial guidance of the impeller 5 with respect to the pump housing 2. In addition to centering and compensation for play, the impeller 8 also enables a good seal between the suction side and the pressure side and at the same time low friction losses.
  • the impeller protector 8 is made of a plastic, such as POM or PTFE, and is accordingly corrosion-resistant. A rusting of the impeller 5 on the impeller seat 10 is therefore not to be feared even in the case of longer downtimes.
  • the impeller protector 8 rests with an end face 12 against a stop 13 of the pump housing 2, which is formed by a circumferential web of the pump housing 2 which projects radially inwards.
  • the axial position of the impeller protector 8 within the pump housing 2 is therefore predetermined by positive locking. As a result, the impeller protector 8 is securely and tightly sealed in the pump housing 2.
  • FIG 2 the arrangement of the impeller protector 8 within the pump housing 2 and the impeller 5 is shown in an enlarged view.
  • the impeller seat 10 is the interface between the insertion area 7 of the impeller 5 and a radial inside of the impeller protector 8 with an axial upper side of the collar 9. This results in a relatively large contact surface, through which a good seal is achieved.
  • the material used for the impeller protector 8 keeps friction low, so that overall a high degree of efficiency can be achieved.
  • a radial seal 15 is arranged in an annular groove 14 of the impeller protector 8 and seals the impeller protector 8 radially with respect to the pump housing 2.
  • the radial seal 15 has on its radial outer side a sealing lip 16 which bears on the pump housing 2 with a suction-side surface 17.
  • the sealing lip 16 thus extends at an angle to the axial direction of the motor shaft 6.
  • the radial seal 15 or the sealing lip 16 bridges a gap 18 which is annular between the impeller protector 8 and the pump housing 2.
  • the impeller protector 8 can thereby be aligned with respect to its radial position within the pump housing 2 and thus compensate for tolerances between the position of the impeller 5 and the pump housing 2.
  • the impeller protector 8 can thus always be exactly centered.
  • a holding force can be generated by the radial seal 15 in that the radial seal 15 is radially clamped between the impeller protector 8 and the pump housing 2. This leads to a non-positive fastening of the impeller protector 8 in the pump housing 2.
  • a groove opening 19 is smaller than a groove base 20. This is achieved by side flanks 21, 22 of the annular groove 14 which are inclined towards one another. The radial seal 15 can thereby be positively received within the annular groove 14, so that the position of the radial seal 15 relative to the impeller protector 8 is clearly defined. There is also a large sealing surface between the radial seal 15 and the impeller protector 8 and thus a good seal.
  • a radial outer edge 23 of the end face 12 of the impeller protector 8 has a bevel through which the impeller protector 8 can be inserted more easily into the pump housing 2. In addition, a geometric over-determination is avoided.
  • the impeller protector 8 is shown in a three-dimensional representation.
  • the radial seal 15 is received in the annular groove 14, which is formed in the peripheral surface of the impeller protector 8.
  • the circumferential collar 9, which forms part of the impeller seat 10, is the End face 12 assigned so that a sufficient guide surface in the radial and axial direction is available for the impeller 5 within the impeller protector 8.
  • the impeller protector provides a flexible seal between the impeller seat and the impeller. This results in a maximum seal, avoiding disadvantageous bypasses between a pressure side and a suction side.
  • wear protection is provided because the impeller protector protects the coating of the pump housing.
  • the impeller protector prevents direct contact between the impeller and the pump housing.
  • the impeller protector in which the impeller is slidably mounted, enables very low-friction movement of the impeller.
  • rusting of the impeller in the pump housing is prevented by the impeller protector being made from a non-rusting material such as plastic.
  • a radial seal, in particular with a sealing lip also achieves a high level of tightness between the impeller protector and the pump housing, while at the same time ensuring play compensation.
  • the impeller protector enables the impeller to rotate almost without wear, which can be completely coated, within the pump housing. Thanks to the good sealing, the efficiency of the pump is further improved. Another advantage is the maintenance of the centrifugal pumps. For example, a simple replacement of the impeller seat is possible by replacing the impeller protector without damaging the coated surfaces of the pump housing. There are no unpleasant grinding noises, even when starting up for the first time, but quiet and pleasant operation is achieved.
  • the centrifugal pump according to the invention can also be used with corrosive pump media, such as swimming pool water. It is possible to manufacture the pump housing as a gray cast iron part and to coat all surfaces that come into contact with the pump medium, so that good protection of the material, which is susceptible to corrosion, is achieved. The area of application of these pumps is thus greatly enlarged.

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

Claims (8)

  1. Pompe centrifuge (1) avec un carter de pompe (2), qui présente une entrée (3) côté aspiration et au moins une sortie (4) coté pression, dans laquelle une roue à aubes (5) montée en rotation destinée à transporter un milieu à pomper de l'entrée (3) à la sortie (4) et un siège de roue à aubes (10) est disposé dans le carter de pompe (2), dans lequel le siège de roue à aubes (10) est réalisé dans un protecteur de roue à aubes (8) annulaire composé d'un matériau résistant à la corrosion, qui est logé dans le carter de pompe (2), dans lequel une zone d'introduction (7) de la roue à aubes (5) est entourée radialement par le protecteur de roue à aubes (8), dans lequel un joint d'étanchéité radial (15) est disposé entre le protecteur de roue à aubes (8) et le carter de pompe (2), et dans lequel le joint d'étanchéité radial (15) présente une lèvre d'étanchéité (16), qui est inclinée par rapport à une direction axiale et s'applique avec une surface (17) côté aspiration contre le carter de pompe (2) ou contre le protecteur de roue à aubes (8), caractérisée en ce qu'une rainure annulaire (14), dans laquelle est retenu le joint d'étanchéité radial (15), est réalisée dans une surface périphérique du protecteur de roue à aubes (8).
  2. Pompe centrifuge selon la revendication 1, caractérisée en ce que la roue à aubes (5) est guidée radialement et axialement dans le protecteur de roue à aubes (8).
  3. Pompe centrifuge selon la revendication 1 ou 2, caractérisée en ce que le protecteur de roue à aubes (8) présente une collerette (9) faisant saillie radialement vers l'intérieur.
  4. Pompe centrifuge selon l'une quelconque des revendications précédentes, caractérisée en ce que le protecteur de roue à aubes (8) s'applique avec une face frontale (12) contre une butée (13) du carter de pompe (2).
  5. Pompe centrifuge selon la revendication 4, caractérisée en ce que la face frontale (12) du protecteur de roue à aubes (8) est biseautée ou arrondie au moins sur un bord extérieur radial (23).
  6. Pompe centrifuge selon l'une quelconque des revendications précédentes, caractérisée en ce que le protecteur de roue à aubes (8) présente une matière plastique, en particulier POM ou PTFE.
  7. Pompe centrifuge selon l'une quelconque des revendications précédentes, caractérisée en ce qu'une ouverture de rainure (19) de la rainure annulaire (14) est plus petite qu'une base de rainure (20), dans laquelle la rainure annulaire (14) présente en particulier des flancs latéraux (21, 22) inclinés l'un vers l'autre.
  8. Pompe centrifuge selon l'une quelconque des revendications précédentes, caractérisée en ce que le joint d'étanchéité radial (15) est précontraint entre le protecteur de roue à aubes (8) et le carter de pompe (2).
EP13180050.0A 2012-09-07 2013-08-12 Pompe centrifuge comprenant une protection de roue mobile avec une gorge annulaire et un joint radial Active EP2706238B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PL13180050T PL2706238T3 (pl) 2012-09-07 2013-08-12 Pompa wirnikowa zawierająca element zabezpieczający wirnika z rowkiem pierścieniowym i uszczelnieniem promieniowym

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102012108357.6A DE102012108357B4 (de) 2012-09-07 2012-09-07 Kreiselpumpe und Laufradprotektor für Kreiselpumpe

Publications (3)

Publication Number Publication Date
EP2706238A2 EP2706238A2 (fr) 2014-03-12
EP2706238A3 EP2706238A3 (fr) 2017-07-19
EP2706238B1 true EP2706238B1 (fr) 2020-03-04

Family

ID=48951375

Family Applications (1)

Application Number Title Priority Date Filing Date
EP13180050.0A Active EP2706238B1 (fr) 2012-09-07 2013-08-12 Pompe centrifuge comprenant une protection de roue mobile avec une gorge annulaire et un joint radial

Country Status (7)

Country Link
US (1) US9447793B2 (fr)
EP (1) EP2706238B1 (fr)
CA (1) CA2826214C (fr)
DE (1) DE102012108357B4 (fr)
DK (1) DK2706238T3 (fr)
ES (1) ES2795102T3 (fr)
PL (1) PL2706238T3 (fr)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20140261582A1 (en) * 2013-03-14 2014-09-18 General Electric Company Seal ring noise reduction for appliance pump
DE102014226144A1 (de) * 2014-12-16 2016-06-16 Kuka Roboter Gmbh Industrieroboter und Verfahren zum Bewegen eines Roboterarms in einem Reinraum
RU175504U1 (ru) * 2017-02-14 2017-12-07 Общество с ограниченной ответственностью Управляющая компания "МСТ Капитал" Центробежный насос
SE2150088A1 (en) * 2021-01-27 2022-07-28 Metso Outotec Sweden Ab Suction liner and centrifugal pump comprising the same
US11486498B1 (en) * 2021-09-10 2022-11-01 Hamilton Sundstrand Corporation Dynamic sealing labyrinth seals

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US3512788A (en) * 1967-11-01 1970-05-19 Allis Chalmers Mfg Co Self-adjusting wearing rings
SE381497B (sv) * 1975-02-10 1975-12-08 Stenberg Flygt Ab Anordning for balansering av radialkrafter i centrifugalpumpar
DE8115273U1 (de) * 1981-05-22 1981-08-13 Hermetic-Pumpen Gmbh, 7803 Gundelfingen "kreiselpumpe mit spaltohr-magnetkupplungs-antrieb"
US4923124A (en) * 1985-01-31 1990-05-08 Microfuel Corporation Method of pneumatic comminution
DE3708956C1 (de) * 1987-03-19 1988-03-17 Handtmann Albert Elteka Gmbh Spaltringdichtung einer Kreiselpumpe
GB2213541B (en) * 1987-12-10 1991-12-11 Sundstrand Corp Mechanical shaft seal
US4948336A (en) * 1987-12-10 1990-08-14 Sundstrand Corporation Mechanical shaft seal
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AUPN143795A0 (en) * 1995-03-01 1995-03-23 Sykes Pumps Australia Pty Limited Centrifugal pump
US6234748B1 (en) * 1998-10-29 2001-05-22 Innovative Mag-Drive, L.L.C. Wear ring assembly for a centrifugal pump
DE19960160B4 (de) * 1999-12-14 2014-09-11 Mahle International Gmbh Vorrichtung zur Optimierung der Spaltweite bei Kreiselpumpen
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Also Published As

Publication number Publication date
PL2706238T3 (pl) 2020-10-05
DE102012108357A1 (de) 2014-03-13
US20140072424A1 (en) 2014-03-13
DE102012108357B4 (de) 2016-06-02
EP2706238A2 (fr) 2014-03-12
CA2826214C (fr) 2020-08-18
EP2706238A3 (fr) 2017-07-19
DK2706238T3 (da) 2020-06-02
US9447793B2 (en) 2016-09-20
ES2795102T3 (es) 2020-11-20
CA2826214A1 (fr) 2014-03-07

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