EP2582983B1 - Pompe centrifuge double flux - Google Patents

Pompe centrifuge double flux Download PDF

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Publication number
EP2582983B1
EP2582983B1 EP11723310.6A EP11723310A EP2582983B1 EP 2582983 B1 EP2582983 B1 EP 2582983B1 EP 11723310 A EP11723310 A EP 11723310A EP 2582983 B1 EP2582983 B1 EP 2582983B1
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EP
European Patent Office
Prior art keywords
impeller
pump
sealing
gaps
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.)
Not-in-force
Application number
EP11723310.6A
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German (de)
English (en)
Other versions
EP2582983A1 (fr
Inventor
Manfred Britsch
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.)
Allweiler GmbH
Original Assignee
Allweiler GmbH
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Filing date
Publication date
Application filed by Allweiler GmbH filed Critical Allweiler GmbH
Publication of EP2582983A1 publication Critical patent/EP2582983A1/fr
Application granted granted Critical
Publication of EP2582983B1 publication Critical patent/EP2582983B1/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
    • F04D1/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D1/006—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps double suction 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
    • F04D1/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal 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
    • F04D29/086—Sealings 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
    • 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
    • F04D29/406—Casings; Connections of working fluid 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
    • F05D2210/00—Working fluids
    • F05D2210/10—Kind or type
    • F05D2210/11—Kind or type liquid, i.e. incompressible
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S415/00—Rotary kinetic fluid motors or pumps
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S417/00—Pumps

Definitions

  • the invention relates to a, preferably single-stage, double-flow centrifugal pump, in particular a cooling water pump for a marine diesel engine or a Balastwasser formulapumpe on a ship, according to the preamble of claim 1. Further, the invention relates to a use according to claim 9.
  • sealing gaps extend in the axial direction and are formed between the impeller and the pump housing.
  • a resulting radial force component acting on the cantilevered shaft occurs, so that the shaft is deflected in the radial direction with the impeller fixed to it in a rotationally fixed manner.
  • the sealing gaps formed as axial gaps must be dimensioned correspondingly broad.
  • centrifugal pumps are suitable, if the shaft is mounted on one side, only for applications in which comparatively low volume flows have to be conveyed.
  • the impeller bearing shaft is usually mounted on both axial sides of the impeller to minimize the radial deflection movement during operation.
  • a shaft with a correspondingly large diameter and / or complex storage would have to be used.
  • centrifugal pump for conveying small volume flows known.
  • the centrifugal pump has sealing gaps between the impeller and a position-variable, ie non-stationary pump component.
  • the known centrifugal pump is not suitable for use on ships.
  • the GB 242230 A also shows a centrifugal pump, wherein the Dichtspaltany between the impeller and a non-stationary component is adjustable.
  • the present invention seeks to provide a double-flow centrifugal pump, for large volume flows of at least 500m 3 / h, especially for use on ships, with a high efficiency without complex design measures is possible.
  • the impeller bearing shaft of the centrifugal pump should be stored exclusively on one side and have the smallest possible diameter. A striking of the impeller on the pump housing should be safely avoided.
  • the invention is based on the idea that the sealing gaps between the impeller and at least one pump part, with which the suction side of the centrifugal pump is sealed against the pressure side, extending in the radial direction with respect to their longitudinal extent, ie as an axial gap train.
  • the impeller according to the invention by means of the sealing gaps in the axial direction spaced from the at least one, preferably exclusively a pump component, ie, a stationary pump housing and / or a stationary built-in part.
  • the at least approximately in the axial direction extending width of the sealing gap, at least at one point, preferably over its longitudinal extent less than the distance between the impeller and all other radially spaced from the impeller components of the pump.
  • the gap width of the sealing gap is smaller than the radial distance of the impeller to all components of the pumps located radially outside the impeller.
  • the sealing gaps are characterized by the fact that their axial extent is (substantially) less than their radial extent.
  • the gap width of the axial gap (sealing gap) measured in the axial direction is preferably greater than the gap width measured in the radial direction of a radial gap arranged between the impeller and the pump component bounding the axial gap.
  • the centrifugal pump according to the invention is designed for large-volume, in particular marine applications.
  • the centrifugal pump for conveying a volume flow from a value range between about 500m 3 / h and about 4000m 3 / h, preferably between about 800m 3 / h and about 1500m 3 / h (for example, smaller cooling water pumps) or between about 1500m 3 / h and about 2300m 3 / h (for example, in medium-sized cooling water pumps) or between 2300m 3 / h and 3500m 3 / h (for example, larger cooling water pump) designed preferably at a maximum head from a range between about 20m and about 50m, preferably from about 30m.
  • the double-flow centrifugal pump is realized in a vertical design, that is to say in such a way that the shaft runs perpendicular to a stationary surface of the centrifugal pump.
  • the impeller bearing shaft is supported only on one side, preferably on an upper side.
  • the gap width of the sealing gaps is at least 20%, preferably at least 12%, more preferably 6% of the radial distance of the impeller 7 to the axial gap defining pump component, i. the pump housing and / or to the, preferably a housing portion forming, insert part.
  • sealing gaps each formed as an axial gap.
  • the sealing gaps are arranged in a region radially inwardly of circumferentially closed radial gaps, via which the impeller is spaced from the at least one, preferably only one, pump component. It is particularly preferred if the axial gaps, starting from the radial gaps in the radial direction extend inwards. Particularly preferred is therefore an embodiment variant in which the axial gaps, at least in a radially inner region, have a smaller distance from the shaft than the radial gaps.
  • the sealing gaps are located within an imaginary circular cylinder whose lateral surface receives the radial gaps in itself. Due to such a variant, the sealing effect is improved.
  • the impeller has a circular cylindrical envelope contour, wherein it is even more preferred if the sealing gaps (axial gaps) between each end face of a cylindrical envelope contour having impeller and the at least one, preferably exclusively one, pump component are formed.
  • an envelope contour can also be provided in which the impeller extends with its outlet region farther outward in the radial direction.
  • the axial sealing gap is arranged in a region which has a smaller radius than a possible radial gap, which is arranged between the pump jet and the impeller.
  • the sealing gaps Due to the inventive design of the sealing gaps as axial gaps, it is possible to measure the gap width of the sealing gaps much lower than in the prior art, without the risk that the impeller strikes at a radial deflection of the sealing gap limiting pump component. It is thus possible to achieve a high efficiency of the centrifugal pump by the inventive design of the sealing gaps, since the amount of liquid flowing from the pressure region in the suction region (negative pressure region) is minimized by the small gap width of the sealing gaps. In the radial direction, the distance between the impeller and the pump component and / or other components of the pump can be dimensioned so that there is no risk of collision even with the largest possible occurring during operation deflection of the impeller.
  • the sealing gaps - within the tolerances - exactly in relation to their longitudinal extent in the radial direction is also a slightly curved or slightly oblique configuration of the sealing gaps by a corresponding formation of at least one of the sealing gaps bounding component (impeller and / or pump component, in particular pump housing) possible, in particular such that the gap geometry of the curved deflection movement of the impeller, especially in unilateral shaft bearing follows, so that the gap width, regardless of the degree of deflection of the impeller in operation, at least independently remains constant.
  • the radius of curvature at least approximately corresponds to the distance of the impeller to the bearing of the impeller bearing shaft.
  • the gap width of the sealing gaps designed as axial gaps is selected from a value range between 200 ⁇ m and 2000 ⁇ m, very particularly preferably between 200 ⁇ m and 400 ⁇ m.
  • the minimum, i. the smallest radial distance of the impeller to which the axial gap formed as a sealing column limiting pump component of the centrifugal pump (with stationary impeller) is selected from a range of values between 2mm to 10mm.
  • the distance between the impeller and the aforementioned pump component is preferably greater than the distances of the specified range of values.
  • the aforementioned minimum radial distance is not only the minimum radial distance of the impeller to the at least one, preferably only a sealing column defining pump component, but the minimum radial distance of the impeller to all components of the pump to a collision at radial To prevent deflection safely.
  • An embodiment of the double-flow centrifugal pump in which the sealing gaps are arranged between the end faces of the impeller pointing in the axial direction and the at least one pump component is particularly preferred.
  • the sealing gaps have the greatest possible axial distance from each other.
  • the impeller has an at least approximately circular cylindrical envelope contour.
  • Especially preferred encloses an imaginary, the radial gaps receiving circular cylindrical surface, the axial gaps radially outward.
  • an axial gap (sealing gap) extending in the radial direction is understood to mean not only an embodiment in which the sealing gaps extend exactly in the radial direction with respect to their longitudinal extent, ie they are, for example, annular disk-shaped.
  • An embodiment is also conceivable in which the sealing gaps have a small pitch angle or are slightly curved, i. have a large radius of curvature, which preferably, at least approximately, in particular in one-sided bearing shaft, corresponds to the distance of the respective sealing gap of the shaft bearing.
  • the respective sealing gap is then designed such that the gap width during operation of the centrifugal pump, ie not with a possible radial deflection of the impeller, or only slightly as possible, since the gap geometry follows the deflection movement.
  • the curvature or bevel of the sealing gaps can be realized by a corresponding geometric shape of the impeller and / or the at least one, preferably only one, the sealing gaps on the opposite axial side of the impeller pump component.
  • the angle (inclination angle) of the respective sealing gap to an imaginary, arranged orthogonal to the longitudinal extent of the shaft radial plane is selected from a range of values between 0.01 ° and 2.0 °.
  • a possible radius of curvature is selected from a value range between 200 mm and 1000 mm, preferably 300 mm and 700 mm.
  • the radius of curvature of the respective sealing gap preferably corresponds, at least approximately, to the distance of the respective sealing gap (in particular at a radially innermost region of the sealing gap) to the shaft bearing, in particular on one side stored (pump shaft). Accordingly, the angle of inclination of the gap explained in the description refers to the inclination of at least one of them Sealing gap limiting surface (of the impeller and / or the pump component) relative to the aforementioned radial plane.
  • centrifugal pump is a single-stage centrifugal pump, that is to say exclusively an impeller.
  • the pump housing is a so-called spiral housing, which predetermines the flow path on the suction side to the two axial sides of the impeller and preferably spirally combines two outlet channels on the pressure side.
  • the invention also leads to the use of a trained according to the concept of the invention double-flow centrifugal pump as a cooling water pump for a marine diesel engine or ballast water pump on a ship.
  • Fig. 1 is a sectional view of a double-flow centrifugal pump 1 shown in a vertical design.
  • a cooling water pump for a marine diesel engine which is designed to promote a flow rate of 2300m3 / h at a maximum head of 30m.
  • the centrifugal pump 1 comprises a pump housing 2 designed as a spiral housing with a suction-side inlet 3 and a pressure-side outlet 4.
  • a shaft 5 mounted on one side, which is mounted by means of a bearing 6 designed as a ball bearing
  • the end of the shaft 5 carries a doppelflutiges impeller 7 with a substantially circular cylindrical envelope contour.
  • the impeller 7 is rotatably mounted on the shaft 5.
  • a shaft seal 8 In a region axially between the bearing 6 and the impeller 7 is a shaft seal 8.
  • the shaft 5 passes through in a region above the shaft seal 8 fixed to the pump housing 2 by screwing cover. 9
  • the impeller 7 separates a negative pressure region 10 (suction side) from an overpressure region 11 (pressure side).
  • the shaft 5 is rotatable by means of a motor, not shown, in particular an electric motor in a conventional manner, said rotating with the shaft 5 impeller 7 from both axial sides of the negative pressure region 10 fluid, here sucking cooling water and in the radial direction outwardly into the overpressure region 11 promotes, wherein the pressure area 11 is divided into two spirally arranged flow channels 12, 13 which are separated by a partition 14 from each other. In the region of the outlet 4, the two flow channels 12, 13 or the fluid streams are brought together again.
  • the radial gaps 15, 16 are not designed as sealing gaps by the approximately 5 mm in the exemplary embodiment shown or do not fulfill a sufficient sealing function.
  • the radial gaps are in the form of circular cylinder jacket surfaces. If the radial gaps 15, 16 were the only sealing gaps, the centrifugal pump 1 would have a very poor efficiency due to the comparatively large gap width, since liquid, here cooling water constantly in large quantity through the radial gaps 15, 16 from the overpressure region 11 in the Vacuum range 10 flow and thus would be funded directly in a circle.
  • the pump housing 2 engages the impeller 7 at both axial sides, ie up and down in the radial direction inwards, such that between each end face 17, 18th of the impeller 7 and the pump housing 2 (pump component) formed as an axial gap, extending in terms of its longitudinal extent in the radial direction sealing gap 19, 20 is formed is. It is essential that these sealing gaps 19, 20, measured at their narrowest point, have a smaller gap width than the radial gaps 15, 16.
  • the sealing gaps 19, 20 are located radially inside the radial gaps 15, 16, wherein the radial gaps 15, 16 pass into the sealing gaps 19, 20 and the sealing gaps 19, 20 directly adjoin the radial gaps 15, 15.
  • the gap width of the sealing gaps 19, 20 corresponds to approximately 400 ⁇ m.
  • the sealing gaps 19, 20 are, as explained on the one hand in the axial direction bounded by the impeller 7, in the embodiment shown by one end face 17, 18 of the impeller 7 and opposite of a parallel here to the respective end face 17, 18 aligned wall surface 21, 22nd of the pump housing 2.
  • the end faces 17, 18 are displaced substantially parallel to the wall surfaces 21, 22 of the pump housing 2, so that a collision can not occur here.
  • the radial gaps 15, 16 are, as explained, so broadly dimensioned that a collision with the impeller 7, even at a maximum permissible deflection exits.
  • impeller 2 shown schematically, which is rotatably mounted on a rotatably mounted shaft 5.
  • the impeller 7 is surrounded by a pump component 23, here the pump housing 2, more precisely an insert part 24, which forms part of the pump housing 2.
  • the insert can not be formed and arranged forming part of the housing, ie within the pump housing and that at a distance to a housing outside.
  • sealing gaps 19, 20 are formed between the pump component 23, which may be formed in one or more parts and the impeller 7, more precisely between the end faces 17, 18 of a circular cylindrical envelope contour having impeller 7, here two sealing gaps 19, 20 are formed. These sealing gaps 19, 20 are axial gaps, which are formed axially between the pump component 23 and the impeller 7.
  • the gap width s of the sealing gaps 19, 20 is 400 ⁇ m in the embodiment shown.
  • the two flat annular disc-shaped sealing gaps 19, 20 are spaced apart in the axial direction and u.a. separated from the one or more radial outlet regions of the impeller. 7
  • two radial gaps 15, 16 are provided in addition to the sealing gaps 19, 20 between the impeller 7 and the pump component 23, the gap width a is greater than the gap width s of the sealing gaps.
  • the gap width a with stationary impeller 7 is about 5mm.
  • the sealing gaps 19, 20 are located radially inside the radial gaps 15, 16, that is, they are spaced less far from the shaft 5 than the radial gaps 15, 16.
  • the radial gaps are circular-cylinder-jacket-shaped.
  • the sealing gaps 19, 20 have approximately the shape of a circular disk.
  • the (narrow) radial gaps 15, 16 can also be dispensed with a modified design of the pump component 23.
  • the sealing gaps are axial gaps which essentially extend in the radial direction with respect to their longitudinal extent and whose axial extent is (substantially) less than their radial extent.
  • a sealing gap 19 is formed between the impeller 7 and a pump component 23.
  • the sealing gap 19 delimiting portion of the impeller 7 extends in relation to the longitudinal extent of the shaft exactly in the radial direction, whereas the surface portion of the pump member 23 which limits the sealing gap 19 is slightly inclined with respect to a radial plane, here at an angle ⁇ of ⁇ 1 °. This results in a sealing gap inclination by this angle ⁇ with respect to an imaginary radial plane, in which in the embodiment shown, the illustrated surface portion of the impeller 7 is located.
  • Fig. 4 are both the sealing gap 19 delimiting surface portion of the impeller 7 and the sealing gap 19 opposite limiting surface portion of the pump member 23 inclined with respect to a radial plane, in the embodiment shown both at the same angle ⁇ from here ⁇ 10 °. It is also the realization of different, but similar inclination angle feasible.
  • the area of the impeller 7 bordering the sealing gap 19 lies in a radial plane with respect to the longitudinal extent of the shaft, whereas the surface portion of the pump component 23 delimiting the sealing gap 19 is curved, Preferably, the curvature has a radius which has the sealing gap 19 from the bearing of the shaft 5, not shown.
  • both the sealing gap 19 bounding surfaces as both the impeller 7 and the pump member 23 are slightly curved.
  • Fig. 7 is the sealing gap 19 limiting surface of the impeller 7 flat, but at an angle ⁇ of ⁇ 10 ° inclined to the radial plane, whereas the sealing gap 19 delimiting surface of the pump member 23 is slightly curved and preferably has a radius of curvature of 500mm.

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

Claims (9)

  1. Pompe centrifuge à double flux, en particulier pompe à eau de refroidissement pour un moteur diesel de bateau ou pompe de refoulement d'eau de ballast, comprenant un boîtier de pompe (2) et un rotor à double flux (7) aménagé en rotation solidaire sur un arbre (5) qui peut être entraîné en rotation, avec lequel un fluide peut être aspiré d'une zone de dépression (10) par deux côtés axiaux et peut être acheminé dans la direction radiale dans une zone de surpression (11), dans laquelle la zone de dépression (10) est étanchée vis-à-vis de la zone de surpression (11) au moyen d'au moins deux intervalles d'étanchéité (19, 20) séparés axialement, dans laquelle les intervalles d'étanchéité (19, 20) sont formés par des intervalles axiaux s'étendant dans la direction périphérique ainsi que dans la direction radiale, dont la largeur (s) est plus faible que la distance radiale (a) du rotor (7) à tous les composants agencés à distance radiale du rotor (7),
    caractérisée en ce que :
    la pompe centrifuge est dimensionnée pour acheminer un courant volumique dans une plage de valeurs comprise entre 500 m3/h et 4000 m3/h et est réalisée en structure verticale et
    l'arbre (5) est monté exclusivement d'un côté et les intervalles d'étanchéité (19, 20) sont formés axialement entre le rotor (7) et le boîtier de pompe stationnaire (2) et/ou une pièce rapportée stationnaire (24).
  2. Pompe centrifuge selon la revendication 1, caractérisée en ce que :
    la largeur (s) de l'intervalle d'étanchéité (19, 20) présente une plage de valeurs comprise entre 200 µm et 2000 µm.
  3. Pompe centrifuge selon l'une quelconque des revendications 1 ou 2,
    caractérisée en ce que :
    la distance radiale minimale (a) du rotor (7) au composant de pompage (23) de la pompe centrifuge dans le cadre d'un rotor immobile (7) est choisi dans une plage de valeurs comprise entre 2 mm et 10 mm.
  4. Pompe centrifuge selon l'une quelconque des revendications 1 ou 3,
    caractérisée en ce que :
    les intervalles d'étanchéité (19, 20) sont ménagés entre les parties avant (17, 18) du rotor (7) et du boîtier de pompe (2) ou de la pièce rapportée (24) .
  5. Pompe centrifuge selon l'une quelconque des revendications précédentes,
    caractérisée en ce que :
    les intervalles d'étanchéité (19, 20) sont conformés de manière à s'étendre exactement dans la direction radiale ou incluent avec un plan radial un angle ayant une plage de valeurs comprise entre environ 0 et 1°, de préférence entre 0,5 et 5°, et/ou l'intervalle d'étanchéité (19, 20) présente un rayon de courbure dans une plage de valeurs comprise entre 200 mm et 1000 mm, de préférence entre 300 mm et 700 mm.
  6. Pompe centrifuge selon l'une quelconque des revendications précédentes,
    caractérisée en ce que :
    la pompe centrifuge est dimensionnée pour acheminer un courant volumique dans une plage de valeurs comprise entre 800 m3/h et environ 1500 m3/h ou entre environ 1500 m3/h et environ 2300 m3/h ou entre 2300 m3/h et 3500 m3/h, de préférence à un niveau d'acheminement maximal dans une plage de valeurs comprise entre environ 20 m et environ 50 m, de préférence d'environ 30 m.
  7. Pompe centrifuge selon l'une quelconque des revendications précédentes,
    caractérisée en ce que :
    les deux intervalles d'étanchéité (19, 20), de préférence exclusivement, présentent une distance radiale au rotor (5) plus petite qu'entre le rotor (7) et les intervalles radiaux (15, 16) formées comme composant de pompe.
  8. Pompe centrifuge selon l'une quelconque des revendications précédentes,
    caractérisée en ce que :
    le rotor (7) présente un contour enveloppant cylindrique à base circulaire.
  9. Utilisation d'une pompe centrifuge selon l'une quelconque des revendications précédentes comme pompe d'eau de refroidissement pour un moteur diesel de bateau ou comme pompe de refoulement de ballast.
EP11723310.6A 2010-06-16 2011-05-09 Pompe centrifuge double flux Not-in-force EP2582983B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102010023931A DE102010023931A1 (de) 2010-06-16 2010-06-16 Doppelflutige Kreiselpumpe
PCT/EP2011/057396 WO2011157485A1 (fr) 2010-06-16 2011-05-09 Pompe centrifuge double flux

Publications (2)

Publication Number Publication Date
EP2582983A1 EP2582983A1 (fr) 2013-04-24
EP2582983B1 true EP2582983B1 (fr) 2016-03-30

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Application Number Title Priority Date Filing Date
EP11723310.6A Not-in-force EP2582983B1 (fr) 2010-06-16 2011-05-09 Pompe centrifuge double flux

Country Status (9)

Country Link
US (1) US20130156545A1 (fr)
EP (1) EP2582983B1 (fr)
JP (1) JP5857042B2 (fr)
KR (1) KR101737665B1 (fr)
CN (1) CN103080556B (fr)
DE (1) DE102010023931A1 (fr)
DK (1) DK2582983T3 (fr)
ES (1) ES2569878T3 (fr)
WO (1) WO2011157485A1 (fr)

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* Cited by examiner, † Cited by third party
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CN107676269A (zh) * 2016-08-02 2018-02-09 东山县飞腾机电设备有限公司 一种高效紧凑型自吸双吸泵
RU196811U1 (ru) * 2019-12-17 2020-03-16 Акционерное общество (АО) "Научно-исследовательский институт "Лопастных машин" ("НИИ ЛМ") Центробежный насос с плоским горизонтальным разъемом корпуса

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CN103080556B (zh) 2016-07-13
DE102010023931A1 (de) 2011-12-22
KR101737665B1 (ko) 2017-05-18
EP2582983A1 (fr) 2013-04-24
JP5857042B2 (ja) 2016-02-10
US20130156545A1 (en) 2013-06-20
KR20130131213A (ko) 2013-12-03
ES2569878T3 (es) 2016-05-12
JP2013532252A (ja) 2013-08-15
DK2582983T3 (en) 2016-05-02
CN103080556A (zh) 2013-05-01
WO2011157485A1 (fr) 2011-12-22

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