EP2660473B1 - Pompe à eaux usées - Google Patents

Pompe à eaux usées Download PDF

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Publication number
EP2660473B1
EP2660473B1 EP12166789.3A EP12166789A EP2660473B1 EP 2660473 B1 EP2660473 B1 EP 2660473B1 EP 12166789 A EP12166789 A EP 12166789A EP 2660473 B1 EP2660473 B1 EP 2660473B1
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EP
European Patent Office
Prior art keywords
impeller
water pump
waste water
pump according
seal
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
EP12166789.3A
Other languages
German (de)
English (en)
Other versions
EP2660473A1 (fr
Inventor
Benny Fredslund Hansen
Poul Johannes Henning
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 Holdings AS
Original Assignee
Grundfos Holdings 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 Holdings AS filed Critical Grundfos Holdings AS
Priority to EP12166789.3A priority Critical patent/EP2660473B1/fr
Priority to US13/886,479 priority patent/US9500204B2/en
Priority to CN201310161745.1A priority patent/CN103382939B/zh
Publication of EP2660473A1 publication Critical patent/EP2660473A1/fr
Application granted granted Critical
Publication of EP2660473B1 publication Critical patent/EP2660473B1/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
    • F04D29/10—Shaft sealings
    • F04D29/106—Shaft 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
    • F04D7/00—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts
    • F04D7/02—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts of centrifugal type
    • F04D7/04—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts of centrifugal type the fluids being viscous or non-homogenous
    • F04D7/045—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts of centrifugal type the fluids being viscous or non-homogenous with means for comminuting, mixing stirring or otherwise treating
    • 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

  • the invention relates to a dirty water pump with the features specified in the preamble of claim 1.
  • Dirty water pumps which may be designed in particular as submersible pumps, are used for pumping out sewage or wastewater, such wastewaters being frequently mixed with solids. These pumps are usually equipped with a single-channel or a multi-channel impeller for conveying the waste water. Such pumps are for example off EP 1 300 594 B1 and WO 2011/079892 known.
  • the solids contained in the effluents can lead to a blockage of the impeller.
  • these solids can accumulate in a Radreteraum on the outside of the impeller and then can lead to a blockage of the impeller.
  • DE 199 60 160 A1 discloses a pump with an impeller having a suction mouth with a surrounding radially directed sealing surface. This sealing surface is applied to a stationary seal, wherein the seal is supported on a radially surrounding webs on a surrounding housing.
  • the dirty water pump according to the invention has at least one impeller, preferably only one impeller.
  • the impeller is driven in rotation in a known manner via a drive motor.
  • the drive motor preferably an electric motor, be integrated with the dirty water pump to a pump unit, in particular in the form of a submersible pump unit.
  • the impeller has a central suction mouth, through which the water to be pumped is sucked.
  • the dirty water pump according to the invention is not necessarily limited to the conveyance of water in the true sense.
  • the dirty water pump according to the invention could also be used to promote other liquids use.
  • the suction mouth is surrounded by an annular sealing surface.
  • the sealing surface is preferably substantially cylindrical or conical. The sealing surface seals against a stationary seal held in a surrounding pump housing or volute.
  • At least one groove is formed in the sealing surface, which groove extends beyond the abutment region of the seal on the sealing surface.
  • the groove preferably extends with its two opposite longitudinal ends beyond the contact region of the seal.
  • the groove communicates with a first end, ie longitudinal end, with the Radnerraum and with a second opposite end or longitudinal end with the suction side of the impeller in combination.
  • the Raddataraum is the area inside the pump or Spirolgephases, which surrounds the impeller in the region of the side of the seal or sealing surface facing away from the suction mouth.
  • the Raderraum thus lies between the suction side and the pressure side of the impeller in its peripheral region and thus forms an intermediate pressure chamber, in which usually a lower pressure than in the pressure chamber of the spiral housing, ie in the outlet region of the impeller, and a higher pressure than on the suction side of the impeller prevails , In this room there is a particular danger that solids or impurities can accumulate and then lead to a blockage of the impeller. Due to the at least one groove, which connects this Radateraum with the suction side of the impeller through the sealing gap between the sealing surface and seal, it is possible that such solids or impurities through the groove are fed back to the suction side of the impeller and so from the Radforceraum be removed.
  • each groove is formed independently of each other, d. H. they do not communicate with each other and each groove has an end which is open to the Radumbleraum and an opposite end, which is open to the suction side of the impeller out.
  • two such grooves may be formed in the sealing surface.
  • the sealing surface may be formed on the impeller itself or formed on a component connected to the impeller.
  • the sealing surface may for example be located on a wear ring, which is connected to the impeller, in particular interchangeable with the impeller is connected.
  • means for generating turbulence are arranged in the wheel side space adjoining the seal. These means for generating turbulence cause the liquid or the water is kept in the Radumbleraum with the impurities or solids contained in motion, that is swirled. This ensures that the solids or impurities do not accumulate or agglomerate, but rather individually or in small quantities can enter together with the liquid in the grooves described, fed back to the suction side of the impeller by the pressure difference between Radacheraum and suction side become.
  • the means for generating turbulence thus improve the removal of solids from the Radacheraum and prevent their accumulation or accumulation, which would no longer allow a discharge or passage through the grooves described.
  • the grooves in order not to unduly affect the sealing property between the seal and the sealing surface, can not be made arbitrarily large.
  • the grooves have a width between 1 and 8 mm, preferably between 2 and 5 mm, and a depth between 0.5 and 3 mm, more preferably between 1 and 2 mm.
  • projections and / or depressions may be formed in the walls of the pump housing adjoining the wheel side space.
  • projections and / or recesses could also be present in the outer surface of the impeller adjoining the wheel side space.
  • the means for generating turbulence are particularly preferably formed on the seal. This allows a particularly favorable production, since no additional components are required, but only the seal must be designed accordingly and with insertion of the seal in a surrounding pump or volute Also equal to the means for generating turbulence in the Radreteraum be introduced.
  • the means for generating turbulence formed on the seal can also be formed as projections and / or depressions.
  • the means for generating the turbulence may be formed exclusively on the seal.
  • the seal is provided on a side facing the Radierraum with a structured or wavy surface. Due to the structure or waveform of the surface turbulence is generated in the Radierraum.
  • the structure may be formed, for example, in the form of elevations or depressions on the surface of the seal.
  • the Radierraum is bounded on one side by the outside of the impeller. As a result of the rotation of the impeller, a movement in the circumferential direction is likewise produced in the liquid in the wheel side space. As the liquid now overflows the structured or undulating surface of the seal, turbulence is created in the wheel side space, which results in a swirling or dispersion of solids and contaminants and prevents accumulation of these solids and contaminants.
  • the structure on the surface of the gasket may be a uniform or unevenly distributed around the circumference shaping or waveform to produce the desired turbulence.
  • the height of the waves ie the distance between wave trough and wave peak, is chosen so that the desired turbulence and turbulence are achieved.
  • the height of these waves can be between 0 and 10 mm. Preference is given to several peaks, for example eight peaks, over the circumference arranged distributed. However, other numbers of waves are conceivable.
  • the waveform preferably has rounded edges as a whole, but generally includes an angular waveform as well.
  • the waves have their maximum height on the inner circumference of the seal and flat to the outer periphery out, d. H. the wave crests and / or the wave troughs extend inclined towards the outer circumference, for example at an angle between 6 and 12 °, more preferably between 8 and 10 ° to a cross-sectional plane which extends normal to the axis of rotation of the impeller.
  • the sealing gap between the seal and the sealing surface is preferably less than 1 mm, more preferably less than 0.75 mm.
  • the seal is preferably made of an elastomer, for example nitrile rubber. In such a material, the wavy surface can be formed very easily.
  • the entire seal can be manufactured with the structured or wavy surface, for example by injection molding. Thus, the wavy surface can be formed very easily.
  • the sealing surface is preferably formed on an outer circumferential surface of the impeller or of the suction mouth of the impeller and is surrounded on the outside by the seal.
  • the sealing gap between the seal and the sealing surface is thus preferably substantially cylindrical, optionally conical, and extends transversely to a cross-sectional plane which intersects the axis of rotation at right angles.
  • the sealing surface and the seal are thus preferably radially opposite each other, wherein the sealing surface is located radially inwardly and the seal is located radially outward. Ie. the sealing surface is the Facing away from the axis of rotation, while the surface of the seal, which bears against the sealing surface, facing the axis of rotation.
  • the at least one groove in the sealing surface expediently extends in the direction of rotation of the impeller.
  • the groove extends inclined to a cross-sectional plane, the cross-sectional plane extending normal to the axis of rotation of the impeller.
  • the groove is inclined so that it does not extend parallel to the axis of rotation.
  • the groove is inclined at an angle between 5 and 20 °, preferably between 6 and 10 ° with respect to said cross-sectional plane.
  • the groove preferably extends such that the front end in the circumferential direction of the groove faces the Radacheraum. Because of this inclination of the groove and the pressure difference between Radquestraum and suction side of the impeller impurities or solids move from the Radacheraum through the groove to the suction side of the impeller and back into the suction of the impeller.
  • the groove does not extend completely around the impeller, but only in a peripheral portion of the sealing surface. In this way, a relatively short distance from the Radreteraum to the suction side of the impeller through the groove is created, which promotes the transport of solids to the suction side of the impeller out.
  • the groove can be made larger.
  • means for dividing solids, in particular fibers are also provided. These are preferably arranged or formed in an annular gap, which connects the wheel side space with a spiral or pressure space surrounding the wheel. This ensures that solids or fibers, before they enter from the pressure or spiral space in the Radierraum, are first crushed. These minced solids are then removed by the means for generating kept in turbulence in the Radierraum in motion, so that accumulation or clumping of these solids in parts of Radmoversraumes is prevented and the solids can be conveyed with liquid through the grooves in the sealing surface through back to the suction side of the impeller.
  • the annular gap preferably forms the lower annular gap of the impeller, which the pressure space of the impeller towards the bottom, d. H. seals to the suction mouth and the Radumbleraum.
  • This annular gap can be designed as a labyrinth seal or part of a labyrinth seal or act.
  • the annular gap is preferably formed between an outer annular surface on the circumference or outer circumference of the impeller and a radially opposite inner peripheral surface of a pump or volute casing surrounding the impeller.
  • the means for dividing solids is further preferably formed by at least one in the annular surface radially inwardly directed recess.
  • the outer ring surface on the impeller has at least one recess, which is directed radially inward and is open towards the outer periphery.
  • a recess is formed in the annular surface.
  • the recess is preferably shaped so that it has a constant cross-section over its axial extent in the direction of the longitudinal or rotational axis.
  • the shape of the groove is preferably substantially cylindrical, preferably in the form of a half-circular cylinder, d. H. formed with a semicircular cross-section.
  • a plurality of radially inwardly directed recesses are formed in the annular surface, which are preferably distributed uniformly over the circumference.
  • the recesses are in the process formed previously described manner. For example, four such recesses may be evenly distributed over the circumference.
  • a radially outwardly directed recess is preferably formed in the inner peripheral surface of the spiral or pump housing opposite the annular surface. Ie. in this inner peripheral surface, a recess is formed, which is open to the inner periphery. This recess, too, preferably has a constant cross-section over its axial extent parallel to the axis of rotation.
  • the recess is also preferably cylindrical, in particular in the form of a half-circular cylinder formed with a semicircular cross-section.
  • This groove is preferably located in a region of the spiral housing, in which the pressure difference between the pressure chamber on the outlet side of the impeller and the Radonceraum is minimized.
  • the recess is therefore preferably located in the inner peripheral surface in the region of that circumferential end of the spiral space, which faces away from an outlet. This is the area in which there is the least pressure in the spiral space, and thus the lowest pressure difference between the spiral space, which surrounds the outside of the impeller outer circumference, and the Radnerraum. In this way it is prevented that additional impurities are pressed by a high pressure difference in the Radnerraum through this groove.
  • the dirty water pump shown is designed as a submersible pump unit with an electric drive motor 2 and arranged at the lower end of the drive motor 2 pump housing 4.
  • the pump housing 4 is provided on its underside with a central opening 6, which forms the inlet opening and the suction mouth of the pump unit. In the lateral direction, radially to the axis of rotation X, extends a discharge nozzle 8, to which an outlet line is connected.
  • an impeller 10 is arranged, which is designed as a single-channel impeller.
  • the impeller 10 has a suction port 12 on its underside.
  • the suction mouth 12 is surrounded by a concentric with the axis of rotation X extending sealing surface 14, which is formed on the outer circumference of a wear ring 16.
  • the wear ring 16 is placed on the cast wheel 10 at the axial end and can be replaced when worn. Radially opposite, the wear ring 16 concentrically surrounding, in the pump housing 4, the opening 6 surrounding a seal in the form of a sealing ring 18 is arranged.
  • the sealing ring 18 bears with an inner circumference 19 in the form of a sealing lip on the sealing surface 14 sealingly.
  • the sealing ring 18 is made of an elastomeric material and has a metal core for dimensional stability.
  • the sealing ring 18 is exchangeable. He seals over the system on the sealing surface 14 from the suction region of the impeller 10 relative to the adjoining Radreteraum 20.
  • the Radweraum 20 surrounds the adjacent to the suction port 12 axial end of the impeller 10 and forms an intermediate pressure chamber.
  • the Raderraum 20 thus lies in the axial direction X between the suction port 12 and the outlet portion 22 of the impeller 10.
  • the outlet region 22 of the impeller 10 is circumferentially surrounded by a pressure or spiral space 24, which is in communication with the pressure port 8.
  • the spiral space 24 is separated from the Radreteraum 20 by an annular gap 26.
  • the wear ring 16 on the sealing surface 14th provided with two diametrically opposed grooves 28.
  • the grooves 28 extend in the circumferential direction inclined over the sealing surfaces 14. In this case, the grooves 28 are inclined so that they extend inclined to a plane perpendicular to the axis of rotation X cross-sectional plane.
  • a first longitudinal end 30 of the opposite second longitudinal end 32 of the groove 28 in the axial direction X is spaced by a dimension which is greater than the axial abutment region between the inner periphery of the seal 18 and the sealing surface 14.
  • the groove 28 to the outer periphery ie facing the seal 18, opened.
  • the first longitudinal end 30 of the groove 28 is open to the Radreteraum 20, while the second longitudinal end 32 is open to the suction side, ie to the opening 6 of the housing 4.
  • the groove 28 thus establishes a connection between the suction side and the wheel side space 20.
  • the inclination of the groove 28 is selected so that in the direction of rotation D, the first longitudinal end 30 is the front end of the groove 28.
  • a second measure essential to the invention is the arrangement of means for generating turbulence in the interior of the Radnnenraumes 20.
  • the means for generating turbulence in this example, a wave-shaped axial surface 34 of the sealing ring 18.
  • the axial surface 34 of the sealing ring 18 limits the Radweraum 20 their lower end.
  • the surface 34 is provided with alternating troughs 36 and crests 38.
  • the wave troughs 36 and wave mountains 38 are distributed uniformly over the circumference of the sealing ring 18.
  • the wave troughs 36 are formed so that they extend from the outer periphery of the sealing ring 18 obliquely to the axis of rotation X. Ie.
  • the wave troughs 36 and peaks 38 have on the inner circumference of the axial surface 34 their maximum height. Ie. the axial distance between wave troughs 36 and wave crests 38 is at the inner periphery of the surface 34 maximum. There is essentially no waveform on the outer circumference. Ie. the wave troughs 36 extend downwardly from the outer periphery of the surface 34 toward the inner circumference. The wave crests 38 lie in a plane with the outer circumference of the surface 34.
  • the wave shape of the surface 34 results in turbulence in the impeller side space 20 as the impeller 10 rotates, which results in circumferential movement of the liquid in the impeller side space 20.
  • Such solids and contaminants can be dissipated individually through the grooves 28 without settling in the Radreteraum 20.
  • a third measure is the arrangement of means for crushing solids in the region of the annular gap 26 between the spiral space 24 and the Radierraum 20.
  • the means for comminuting solids are formed by four recesses 40 which are formed in an annular surface 42 which the annular gap 26 limited to its inner circumference.
  • the annular surface 42 on the outer circumference of the impeller 10 is radially opposite an inner peripheral surface 44 of the pump housing 4, so that the inner peripheral surface 44 limits the annular gap 26 on its outer periphery.
  • the recesses 40 are directed radially inwards and have a semicircular cross-section.
  • the recesses 40 are parallel over their axial length to the rotation axis X a constant cross-section, so that they have the shape of a half-circular cylinder.
  • a further recess 46 is arranged beyond.
  • the recess 46 is directed radially outward and open to the inner circumference of the inner peripheral surface 44.
  • the one recess 46 is located so that the recesses 40 sweep the recess 46 during rotation of the impeller 10.
  • a shearing action between the recesses 40 and the recess 46 is achieved, so that impurities, such as fibers, are comminuted between the recesses 40 and the recess 46 by shearing the passage of the annular gap 26, so that the solids in comminuted form in the Radreteraum 20 enter and then exit from this through the grooves 28 later.
  • the one recess 46 on the inner peripheral surface 44 is arranged in the region of the spiral space 20, at which the smallest pressure difference to the Radierraum 20 prevails. This is in the region of the circumferential end 48 of the pressure or spiral space 24, which faces away from the outlet 50 with the pressure port 8 in the circumferential direction. Ie. the recess 46 is spaced in the direction of rotation D of the impeller 10 of the outlet 50 in this example by an angle of about 45 °.

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

Claims (15)

  1. Pompe à eaux usées comprenant une roue mobile (10) qui présente une embouchure d'aspiration (12) pourvue d'une surface d'étanchéité (14) qui entoure celle-ci de façon annulaire et est en appui contre un joint d'étanchéité (18) fixe, caractérisée en ce qu'est formée dans la surface d'étanchéité (14) au moins une rainure (28) qui s'étend au-delà d'une région d'appui du joint d'étanchéité (18) contre la surface d'étanchéité (14) et qui se trouve en relation, par une première extrémité (30), avec un espace latéral de roue (20), et par une seconde extrémité opposée (32) avec le côté aspiration de la roue mobile (10), et en ce que sont disposés dans l'espace latéral de roue (20) adjacent au joint d'étanchéité (18) des moyens (34) destinés à générer des turbulences.
  2. Pompe à eaux usées selon la revendication 1, caractérisée en ce que les moyens (34) sont exécutés pour générer des turbulences au niveau du joint d'étanchéité (18).
  3. Pompe à eaux usées selon la revendication 2, caractérisée en ce que le joint d'étanchéité (18) est pourvu, du côté orienté vers l'espace latéral de roue (20), d'une surface (34) structurée ou ondulée.
  4. Pompe à eaux usées selon la revendication 3, caractérisée en ce que le joint d'étanchéité (18) est de forme annulaire et la surface ondulée (34) est située sur une face avant axiale du joint d'étanchéité (18).
  5. Pompe à eaux usées selon l'une des revendications précédentes, caractérisée en ce que la surface d'étanchéité (14) est réalisée sur une surface périphérique extérieure de la roue mobile (10) et est entourée sur sa périphérie extérieure par le joint d'étanchéité (18).
  6. Pompe à eaux usées selon l'une des revendications précédentes, caractérisée en ce que la surface d'étanchéité (14) et le joint d'étanchéité (18) sont en appui l'un contre l'autre radialement.
  7. Pompe à eaux usées selon l'une des revendications précédentes, caractérisée en ce que la rainure (28), au moins au nombre de une, s'étend de manière inclinée dans le sens de rotation (D) de la roue mobile (10) de façon telle que son extrémité avant (30) dans le sens de rotation (D) est orientée vers l'espace latéral de roue (20).
  8. Pompe à eaux usées selon l'une des revendications précédentes, caractérisée en ce que la rainure (28) s'étend uniquement dans une région partielle périphérique de la surface d'étanchéité (14).
  9. Pompe à eaux usées selon l'une des revendications précédentes, caractérisée en ce que, dans une fente annulaire (26) qui relie l'espace latéral de roue (20) à une chambre en spirale (24) entourant la roue mobile (10), sont formés des moyens (40, 46) destinés au fractionnement de matières solides.
  10. Pompe à eaux usées selon la revendication 9, caractérisée en ce que la fente annulaire (26) est formée entre une surface annulaire extérieure (42) sur le pourtour de la roue mobile (10) et une surface périphérique intérieure (44) radialement opposée d'un boîtier hélicoïdal (4) entourant la roue mobile (10).
  11. Pompe à eaux usées selon la revendication 10, caractérisée en ce qu'au moins un évidement (40) radialement orienté vers l'intérieur est formé dans la surface annulaire (42).
  12. Pompe à eaux usées selon la revendication 11, caractérisée en ce que sont formés dans la surface annulaire (42) plusieurs évidements (40) radialement orientés vers l'intérieur et qui sont répartis, de préférence de façon régulière, sur la périphérie.
  13. Pompe à eaux usées selon l'une des revendications 10 à 12, caractérisée en ce qu'est formé dans la surface périphérique intérieure (44) opposée à la surface annulaire (42) un évidement (46) radialement orienté vers l'extérieur.
  14. Pompe à eaux usées selon la revendication 13, caractérisée en ce que l'évidement (46) est situé dans la surface périphérique intérieure (44) du boîtier hélicoïdal (4), dans la région de l'extrémité périphérique (48) de la chambre en spirale (24) située à l'opposé d'une sortie (50).
  15. Pompe à eaux usées selon l'une des revendications 10 à 14, caractérisée en ce que l'évidement (44 ; 46) a une section transversale de forme semi-circulaire.
EP12166789.3A 2012-05-04 2012-05-04 Pompe à eaux usées Not-in-force EP2660473B1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
EP12166789.3A EP2660473B1 (fr) 2012-05-04 2012-05-04 Pompe à eaux usées
US13/886,479 US9500204B2 (en) 2012-05-04 2013-05-03 Waste water pump
CN201310161745.1A CN103382939B (zh) 2012-05-04 2013-05-06 污水泵

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP12166789.3A EP2660473B1 (fr) 2012-05-04 2012-05-04 Pompe à eaux usées

Publications (2)

Publication Number Publication Date
EP2660473A1 EP2660473A1 (fr) 2013-11-06
EP2660473B1 true EP2660473B1 (fr) 2016-11-23

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EP12166789.3A Not-in-force EP2660473B1 (fr) 2012-05-04 2012-05-04 Pompe à eaux usées

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US (1) US9500204B2 (fr)
EP (1) EP2660473B1 (fr)
CN (1) CN103382939B (fr)

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DE102012205758A1 (de) * 2012-04-10 2013-10-10 Continental Automotive Gmbh Rotierende elektrische Maschine
EP3309404B1 (fr) * 2016-10-14 2022-03-02 Grundfos Holding A/S Pompe d'eau usée
CN107387456A (zh) * 2017-09-04 2017-11-24 河北兴临水泵有限公司 水泵密封装置
DE102019006665A1 (de) * 2019-09-23 2021-03-25 KSB SE & Co. KGaA Einschaufelrad
EP4056852A1 (fr) * 2021-03-09 2022-09-14 Metso Outotec Sweden AB Pompe à boue

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DE20114891U1 (de) 2001-09-10 2001-11-15 Grundfos As Abwasserkreiselpumpe
EP2348220B1 (fr) 2009-12-30 2015-07-08 Grundfos Management A/S Pompe submersible
CN101922453A (zh) * 2010-08-06 2010-12-22 杭州振兴工业泵制造有限公司 长纤维及粗浆输送泵
CN102207091B (zh) * 2011-06-07 2012-12-12 张意立 一种内外拐角喷水高浓度离心纸浆泵

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Publication number Publication date
EP2660473A1 (fr) 2013-11-06
CN103382939B (zh) 2016-06-22
US9500204B2 (en) 2016-11-22
US20130294910A1 (en) 2013-11-07
CN103382939A (zh) 2013-11-06

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