US20130156545A1 - Dual-flow centrifugal pump - Google Patents

Dual-flow centrifugal pump Download PDF

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Publication number
US20130156545A1
US20130156545A1 US13/704,080 US201113704080A US2013156545A1 US 20130156545 A1 US20130156545 A1 US 20130156545A1 US 201113704080 A US201113704080 A US 201113704080A US 2013156545 A1 US2013156545 A1 US 2013156545A1
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US
United States
Prior art keywords
impeller
centrifugal pump
gaps
radial
sealing
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.)
Abandoned
Application number
US13/704,080
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English (en)
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
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 Allweiler GmbH filed Critical Allweiler GmbH
Assigned to ALLWEILER GMBH reassignment ALLWEILER GMBH ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: BRITSCH, MANFRED
Publication of US20130156545A1 publication Critical patent/US20130156545A1/en
Assigned to IMO INDUSTRIES INC., CONSTELLATION PUMPS CORPORATION, ALLOY RODS GLOBAL INC., DISTRIBUTION MINING & EQUIPMENT COMPANY, LLC, TOTAL LUBRICATION MANAGEMENT COMPANY, EMSA HOLDINGS INC., COLFAX CORPORATION, STOODY COMPANY, VICTOR EQUIPMENT COMPANY, VICTOR TECHNOLOGIES INTERNATIONAL, INC., CLARUS FLUID INTELLIGENCE, LLC, THE ESAB GROUP INC., ANDERSON GROUP INC., HOWDEN NORTH AMERICA INC., HOWDEN COMPRESSORS, INC., SHAWEBONE HOLDINGS INC., HOWDEN AMERICAN FAN COMPANY, ESAB AB, HOWDEN GROUP LIMITED, ALCOTEC WIRE CORPORATION reassignment IMO INDUSTRIES INC. RELEASE BY SECURED PARTY (SEE DOCUMENT FOR DETAILS). Assignors: DEUTSCHE BANK AG NEW YORK BRANCH
Abandoned 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
    • 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 ballast water delivery pump on a ship, with a pump housing and with a dual-flow impeller rotationally fixedly arranged on a rotationally driven shaft, with which impeller a fluid can be suctioned from two axial sides from a negative pressure area (suction side) and delivered in the radial direction into a positive pressure area (pressure side), whereby the negative pressure area is sealed off with respect to the positive pressure area by means of at least two sealing gaps which are spaced apart axially (via the positive pressure area) and which are formed between the impeller and at least one stationary pump component, in particular the pump housing.
  • a preferably single-stage, double-flow centrifugal pump in particular a cooling water pump for a marine diesel engine or a ballast water delivery pump on a ship, with a pump housing and with a dual-flow impeller rotationally fixedly arranged on a rotationally
  • the sealing gaps formed as annular gaps, run in the axial direction and are formed between the impeller and the pump housing.
  • a resulting radial force component acting on the shaft supported on one side occurs, in particular if the centrifugal pumps are not operated at their optimal working point, so that the shaft with the impeller rotationally fixed on it is deflected in the radial direction.
  • the sealing gaps formed as axial gaps must be dimensioned to be appropriately wide.
  • centrifugal pumps are only suited for applications, if the shaft is supported on one side, in which comparatively low volume flows are to be delivered.
  • the shaft carrying the impeller is supported as a rule on both axial sides of the impeller in order to minimize the radial deflection movement during operation.
  • a shaft would have to be used with an appropriately large diameter and/or a complex support.
  • the invention solves the basic problem of indicating a dual-flow centrifugal pump, in particular for large-volume flows of at least 500 m 3 /h with which a high degree of efficiency is possible without complex constructive measures.
  • the centrifugal pump shaft carrying the impeller should preferably be supported exclusively on one side and have the smallest possible diameter. A striking of the impeller on the pump housing should be reliably avoided.
  • the sealing gaps are formed as axial gaps extending in the circumferential direction as well as in the radial direction and arranged axially between the pump component and the impeller, the gap width of which gaps, preferably measured in the axial direction, is greater than the radial distances of the impeller to all components that are arranged with radial spacing radially outside of the impeller.
  • the gap width of the sealing gaps formed as axial gaps is greater than the gap widths of all other gaps (radial gaps) that are limited on one side by the impeller. This means, expressed another way, that the distances, measured in the radial direction, between the impeller and any components of the pump are greater than the gap width of the sealing gaps formed as an axial gap.
  • the invention is based on the concept that the sealing gaps between the impeller and at least one pump part with which the suction side of the centrifugal pump is sealed relative to the pressure side are to be constructed running in the radial direction relative to its longitudinal extent, i.e., as an axial gap.
  • the impeller in accordance with the invention is distanced in the axial direction by the sealing gaps from the at least one, preferably exclusively one pump component.
  • the width of the sealing gap, which width extends at least approximately in the axial direction, is less at least at one position, preferably over its longitudinal extent, than the distance between the impeller and all other pump components arranged with a radial distance to the impeller.
  • the gap width of the sealing gap is less than the radial distance of the impeller to all pump components located radially outside of the impeller.
  • the sealing gaps are distinguished in that their axial extent is (considerably) less than their radial extent.
  • the gap width of the axial gap, (sealing gap) measured in the axial direction is greater than the gap width, measured in the radial direction, of a radial gap arranged between the impeller and the pump component limiting the axial gap.
  • the gap width of the sealing gap is preferably at least 20%, more preferably at least 12% and even more preferably 6% of the radial distance of the impeller 7 to the pump component limiting the axial gap, in particular to the pump housing and/or to an insertion part preferably forming a housing section.
  • sealing gaps formed as an axial gap on both axial sides of the radial discharge area of the impeller.
  • a variant of an embodiment is quite especially preferred in which the preferably exclusively two sealing gaps are arranged in an area radially inside circumferentially closed radial gaps via which the impeller is distanced from the at least one, preferably exclusively one pump component. It is especially preferable if the axial gaps extend starting from the radial gaps in the radial direction inward. Therefore, a variant of an embodiment is especially preferred in which the axial gaps have, at least in a radially inner area, a lesser distance to the shaft than the radial gaps do.
  • the sealing gaps are advantageously located inside an imaginary circular cylinder whose generated surface receives the radial gaps. As a result of such a variant of an embodiment the sealing action is improved.
  • the impeller has a circular, cylindrical casing contour, whereby it is even more preferred if the sealing gaps (axial gaps) are formed between a front side of the impeller comprising a cylindrical casing contour and between the at least one, preferably exclusively one pump component.
  • a casing contour can also be provided in which the impeller extends with its discharge area further to the outside in the radial direction.
  • the axial sealing gap is arranged in an area that has a lesser radius than a possible radial gap arranged between the pump jet and the impeller.
  • the sealing gaps Based on the formation of the sealing gaps as axial gaps, it is possible to dimension the gap width of the sealing gaps considerably smaller than in the prior art without there being the danger that the impeller strikes the pump component limiting the sealing gaps upon a radial deflection. It is therefore possible by means of the design of the sealing gaps in accordance with the invention to achieve a high efficiency of the centrifugal pump since the amount of liquid that flows from the pressure area into the suction area (negative pressure area) is minimized by the small gap width of the sealing gaps.
  • the distance between the impeller and the pump component and/or other components of the pump can be dimensioned in the radial direction in such a manner that even in case of the greatest possible deflection of the impeller occurring during operation there is no danger of collision.
  • An embodiment has an especially simple construction and is therefore preferred in which the sealing gaps run—in the framework of the tolerances—exactly in the radial direction relative to their longitudinal extent.
  • a slightly curved or slightly oblique design of the sealing gaps by an appropriate shaping of at least one structural component (impeller and/or pump component, especially pump housing) limiting the sealing gaps is possible, in particular in such a manner that the gap geometry of the curved deflection movement of the impeller takes place especially with a one-sided shaft support so that the gap width remains at least independently constant independently of the degree of the deflection of the impeller during operation.
  • the radius of curvature corresponds in an especially preferred manner at least approximately to the distance of the impeller to the support of the shaft carrying the impeller.
  • the gap width of the sealing gaps formed as axial gaps is selected from a value range between 200 ⁇ m and 2000 ⁇ m, quite especially preferably between 200 ⁇ m and 400 ⁇ m.
  • the minimal, i.e., the slightest radial distance of the impeller to the pump component of the centrifugal pump, which pump component limits the sealing gaps formed as axial gaps, (with the impeller standing still) is selected from a value range between 2 mm to 10 mm.
  • the distance between the impeller and the previously cited pump component is preferably greater than the distances of the indicated value range.
  • the previously cited minimal radial distance is especially preferably not only the minimal radial distance of the impeller to the at least one, preferably exclusively one pump component limiting the sealing gaps, but rather the minimal radial distance of the impeller to all structural components of the pump, in order to reliably prevent a collision upon a radial deflection.
  • An embodiment of the dual-flow centrifugal pump has an especially preferred construction in which the sealing gaps are arranged between the front sides of the impeller, which front sides face in the axial direction, and between the at least one pump component. In other words, it is preferred if the sealing gaps have the greatest possible axial distance from each other.
  • the impeller has a casing contour that is at least approximately circularly cylindrical.
  • An imaginary generated surface of a centrifugal cylinder which surface receives the radial gaps especially preferably surrounds the axial gaps radially on the outside.
  • an axial gap (sealing gap) extending in the radial direction denotes not only an embodiment in which the sealing gaps run exactly in the radial direction relative to the longitudinal extent, in the framework of the tolerances, that is, they are constructed, for example, in the shape of annular disks.
  • An embodiment is also conceivable in which the sealing gaps have a slight angle of rise or are slightly curved, i.e., have a large radius of curvature that preferably corresponds at least approximately, in particular in the case of a shaft supported on one side, to the distance of the particular sealing gap from the shaft support.
  • the particular sealing gap is thus designed in such a manner that the gap width during the operation of the centrifugal pump does not change or changes only as slightly as possible, that is, upon a possible radial deflection of the impeller since the gap geometry follows the deflection movement.
  • the curvature or beveling of the sealing gap can be realized by an appropriate geometric shaping of the impeller and/or of the at least one, preferably exclusively one pump component limiting the sealing gap on the axial side opposite the impeller.
  • the angle (angle of inclination) of the particular sealing gap to an imaginary radial plane arranged orthogonally to the longitudinal extension of the shaft is quite especially preferably selected from a value range between 0.01° and 2.0°.
  • a possible radius of curvature is preferably selected from a value range between 200 mm and 1000 mm, preferably 300 mm and 700 mm.
  • the radius of curvature of the particular sealing gap preferably corresponds at least approximately to the distance of the particular sealing gap (in particular on a radially innermost area of the sealing gap) to the shaft support, in particular in the case of one (pump shaft) supported on one side.
  • the angle of inclination of the gap refers to the angle of at least one surface (of the impeller and/or of the pump component) limiting the sealing gap relative to the previously cited radial plane.
  • the centrifugal pump in accordance with the invention is designed for large-volume flow applications, in particular marine applications.
  • the centrifugal pump is preferably designed for delivering a volume flow from a value range between approximately 500 m 3 /h and approximately 4000 m 3 /h, preferably between approximately 800 m 3 /h and approximately 1500 m 3 /h (for example, in the case of rather small cooling water pumps) or between approximately 1500 m 3 /h and approximately 2300 m 3 /h (for example, in the case of average-size cooling water pumps) or between 2300 m 3 /h and 3500 m 3 /h (for example, in the case of rather large cooling water pumps), preferably at a maximum delivery level from a value range between approximately 20 m and approximately 50 m, preferably from approximately 30 m. It is especially preferable for reasons of space, especially for marine applications, if the dual-flow centrifugal pump is realized in a vertical construction, that is, in such a manner that the shaft runs
  • the centrifugal pump is a single-stage centrifugal pump, that is, a pump comprising exclusively one impeller.
  • the pump housing is a so-called spiral housing that sets the flow path on the suction side to the two axial sides of the impeller and combines preferably two outlet conduits in a helical manner on the pressure side.
  • the invention also comprises the use of a dual-flow centrifugal pump designed in accordance with the concept of the invention as a cooling water pump for a marine diesel engine or as a ballast water delivery pump on a ship.
  • FIG. 1 shows a cross-section view of an exemplary embodiment of a dual-flow centrifugal pump constructed in accordance with the concept of the invention
  • FIG. 2 shows a schematic illustration of gap conditions for the pump of FIG. 1 .
  • FIGS. 3-7 show a plurality of embodiments of the sealing gaps.
  • FIG. 1 shows a sectional view of a dual-flow centrifugal pump 1 in a vertical orientation (i.e., the impeller shaft is oriented vertically).
  • the exemplary embodiment shown is a cooling water pump for a marine diesel engine designed for delivering a volume flow of 2300 m 3 /h at a maximum delivery level of 30 m.
  • the centrifugal pump 1 comprises a pump housing 2 designed as a spiral housing and with a suction-side inlet 3 as well as a pressure-side outlet 4 .
  • a shaft 5 supported on one side extends into the pump housing 2 from above downward in a vertical direction and is supported by a bearing 6 constructed as a ball bearing.
  • the shaft 5 carries on its inside a dual-flow impeller 7 with a substantially circularly cylindrical casing contour.
  • the impeller 7 sits in a rotationally fixed manner on the shaft 5 .
  • a shaft seal 8 is located in an area axially between the support 6 and the impeller 7 . As is apparent from FIG. 1 the shaft 5 extends in an area above the shaft seal 8 through a cover 9 fixed by screwing on the pump housing 2 .
  • the impeller 7 separates a negative pressure area 10 (suction side) from a positive pressure area 11 (pressure side).
  • the shaft 5 can be rotated in a known manner by an engine (not shown), in particular by an electromotor, whereby the impeller 7 rotating with the shaft 5 sucks fluid, here cooling water, from both axial sides out of the negative pressure area 10 and delivers it in a radial direction outward into the positive pressure area 11 , whereby the positive pressure area 11 is subdivided into two helically arranged flow conduits 12 , 13 separated from one another by a dividing wall 14 .
  • the two flow conduits 12 , 13 and the fluid currents are brought together again in the area of the outlet 4 .
  • the radial gaps 15 , 16 are not designed as sealing gaps and fulfill no sufficient sealing function on account of their comparatively large gap width (measured at the narrowest position) from the one in the exemplary embodiment shown of approximately 5 mm.
  • the radial gaps have the form of circular, cylindrical surfaces. If the radial gaps 15 , 16 were the only sealing gaps, the centrifugal pump 1 would have an extremely poor efficiency on account of the comparatively large gap width since liquid, here cooling water, would constantly flow in a large amount through the radial gaps 15 , 16 from the positive pressure area 11 into the negative pressure area 10 and would thus be directly delivered in a circuit.
  • the pump housing 2 extends over the impeller 7 on both axial sides, i.e., above and below in an inward radial direction in such a manner that a sealing gap, 19 , 20 that is constructed as an axial gap and extends as regards its longitudinal extension in the radial direction is formed between each front side 17 , 18 of the impeller 7 and the pump housing 2 (pump component). It is essential that these sealing gaps, 19 , 20 , measured at their narrowest position, 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 , whereby the radial gaps 15 , 16 merge into the sealing gaps, 19 , 20 and the sealing gaps, 19 , 20 border directly on the radial gaps 15 , 16 .
  • the width of the sealing gaps 19 , 20 is about 400 ⁇ m.
  • the sealing gaps, 19 , 20 are, as explained, limited on the one hand in the axial direction by the impeller 7 , in the exemplary embodiment shown by a front side 17 , 18 of the impeller 7 and on the opposing side by a wall surface 21 , 22 of the pump housing 2 , which wall surface is aligned here parallel to the particular front side 17 , 18 .
  • the radial gaps 15 , 16 are, as explained, dimensioned to be so wide that even here a collision with the impeller 7 , even at a maximally admissible deflection, is excluded.
  • FIG. 2 schematically shows the gap conditions.
  • the schematically shown impeller 2 can be recognized, arranged in a rotationally fixed manner on a rotatably supported shaft 5 .
  • the impeller 7 is surrounded by a pump component 23 , here the pump housing 2 , more precisely an inserted part 24 that forms a component of the pump housing 2 .
  • the inserted part 24 may not be constructed and arranged to form a component of the housing, therefore, inside the pump housing and at a distance to an outer housing side.
  • Two sealing gaps 19 , 20 are formed between the pump component 23 , that can be designed to be monopartite or bipartite, and the impeller 7 , more precisely between the front sides 17 , 18 of the impeller 7 comprising a circular, cylindrical casing contour.
  • These sealing gaps 19 , 20 are axial gaps that are formed axially between the pump component 23 and the impeller 7 .
  • the gap widths “s” of the sealing gaps 19 , 20 are 400 ⁇ m in the exemplary embodiment shown.
  • the two sealing gaps 19 , 20 in the form of flat annular disks are distanced from one another in the axial direction and, among other things, separated from one another by the radial outlet area or areas of the impeller 7 .
  • two radial gaps 15 , 16 are provided whose gap width a is greater than the gap width s of the sealing gaps.
  • the gap widths “a” are approximately 5 mm when impeller 7 is at a standstill.
  • the sealing gaps 19 , 20 are located radially inside the radial gaps 15 , 16 and therefore are closer to the shaft 5 (i.e., smaller) than the radial gaps 15 , 16 .
  • the radial gaps have the form of circular, cylindrical jacket.
  • the sealing gaps 19 , 20 have approximately the form of a circular ring disk.
  • sealing gaps 19 , 20 present in parallel planes that are axial gaps on at least one of the two axial sides, preferably on both axial sides of the impeller 7 .
  • two axially adjacent sealing gaps are preferably connected to one another via a radial gap with a larger gap width than the gap width of the sealing gaps on at least one axial side of the impeller 7 .
  • FIGS. 3 to 7 Conceivable alternative sealing gap geometries are shown in the FIGS. 3 to 7 , whereby the angles or radii of curvature are shown in an exaggerated manner for reasons of clarity. In reality, minimal rises and large radii of curvature are involved.
  • sealing gaps are axial gaps that run (as regards their longitudinal extension) substantially in the radial direction and their axial extension is (substantially) less than their radial extension.
  • a sealing gap 19 is formed between the impeller 7 and a pump component 23 .
  • the section of the impeller 7 limiting the sealing gap 19 runs relative to the longitudinal extension of the shaft exactly in the radial direction, whereas on the contrary the surface section of the pump component 23 , that limits the sealing gap 19 , is slightly inclined relative to a radial plane, here under an angle ⁇ of ⁇ 1°. This results in a sealing gap inclination about this angle ⁇ relative to an imaginary radial plane in which in the exemplary embodiment shown the represented surface section of the impeller 7 lies.
  • the surface section of the impeller 7 limiting the sealing gap 19 as well as the surface section of the pump component 23 that is opposite and limits the sealing gap 19 are inclined relative to a radial plane, in the exemplary embodiment shown both under the same angle ⁇ of ⁇ 10° here.
  • the use of different but similar angles of inclination is also possible.
  • the surface area of the impeller 7 limiting the sealing gap 19 is located in a radial plane relative to the longitudinal extension of the shaft, in contrast to which the surface area of the pump component 23 limiting the sealing gap 19 is curved, which curvature preferably has a radius that has the sealing gap 19 from the support of the shaft 5 (not shown).
  • both surfaces limiting the sealing gap 19 as well as the surface of the impeller 7 and the surface of the pump component 23 are designed to be slightly curved.
  • the surface of the impeller 7 limiting the sealing gap 19 is designed level but inclined at an angle ⁇ of ⁇ 10° to the radial plane, in contrast to which the surface of the pump component 23 limiting the sealing gap 19 is slightly curved and preferably has a radius of curvature of 500 mm.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
US13/704,080 2010-06-16 2011-05-09 Dual-flow centrifugal pump Abandoned US20130156545A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102010023931A DE102010023931A1 (de) 2010-06-16 2010-06-16 Doppelflutige Kreiselpumpe
DE102010023931.3 2010-06-16
PCT/EP2011/057396 WO2011157485A1 (de) 2010-06-16 2011-05-09 Doppelflutige kreiselpumpe

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US20130156545A1 true US20130156545A1 (en) 2013-06-20

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US13/704,080 Abandoned US20130156545A1 (en) 2010-06-16 2011-05-09 Dual-flow centrifugal pump

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

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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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EP2582983A1 (de) 2013-04-24
DE102010023931A1 (de) 2011-12-22
DK2582983T3 (en) 2016-05-02
JP2013532252A (ja) 2013-08-15
EP2582983B1 (de) 2016-03-30
CN103080556A (zh) 2013-05-01
CN103080556B (zh) 2016-07-13
JP5857042B2 (ja) 2016-02-10
ES2569878T3 (es) 2016-05-12
KR20130131213A (ko) 2013-12-03
WO2011157485A1 (de) 2011-12-22
KR101737665B1 (ko) 2017-05-18

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