EP0599204B1 - Unité de pompe submersible - Google Patents

Unité de pompe submersible Download PDF

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Publication number
EP0599204B1
EP0599204B1 EP93118605A EP93118605A EP0599204B1 EP 0599204 B1 EP0599204 B1 EP 0599204B1 EP 93118605 A EP93118605 A EP 93118605A EP 93118605 A EP93118605 A EP 93118605A EP 0599204 B1 EP0599204 B1 EP 0599204B1
Authority
EP
European Patent Office
Prior art keywords
housing
submersible pump
pump unit
unit according
flow
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.)
Expired - Lifetime
Application number
EP93118605A
Other languages
German (de)
English (en)
Other versions
EP0599204A1 (fr
Inventor
Niels Due Jensen
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 AS
Original Assignee
Grundfos 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 AS filed Critical Grundfos AS
Publication of EP0599204A1 publication Critical patent/EP0599204A1/fr
Application granted granted Critical
Publication of EP0599204B1 publication Critical patent/EP0599204B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D13/00—Pumping installations or systems
    • F04D13/02—Units comprising pumps and their driving means
    • F04D13/06—Units comprising pumps and their driving means the pump being electrically driven
    • F04D13/08—Units comprising pumps and their driving means the pump being electrically driven for submerged use
    • F04D13/086—Units comprising pumps and their driving means the pump being electrically driven for submerged use the pump and drive motor are both submerged
    • 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
    • F04D29/44—Fluid-guiding means, e.g. diffusers
    • F04D29/445—Fluid-guiding means, e.g. diffusers 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
    • F05D2260/00—Function
    • F05D2260/60—Fluid transfer
    • F05D2260/604—Vortex non-clogging type pumps

Definitions

  • the invention relates to a submersible pump unit with the features specified in the preamble of claim 1.
  • Such a submersible pump unit is described, for example, in EP-A-0 420 218.
  • Such aggregates are e.g. used in the field of wastewater technology. They are used not only to convey pure or contaminated liquids, but also to transport solids carried in the liquid. Such units are therefore designed so that solid parts can be conveyed up to the size of a ball that fits through the inlet opening. They are therefore often e.g. used in the construction or food industry.
  • the impeller In order to allow the passage of large solid parts, it is known to design the impeller as a single-bladed, ducted or free-flow impeller.
  • the inlet opening is usually located on the underside of the pump directly below the impeller.
  • the outlet opening in the form of the pressure port is usually arranged radially to the impeller.
  • Such a pump is known for example from US Pat. No. 4,454,993 or US Pat. No. 4,697,746.
  • these pumps are chipped in the direction of conveyance assigned in front of the impeller, which is to shred the solid particles before entering the area of the pump impeller.
  • Submersible pump units with a concentric housing are also known, from which the fluid is radially discharged and then directed in a bend in the direction parallel to the axis.
  • the submersible pump unit known from EP-A-0 420 218 is more favorable, the pump housing of which is designed as a molded part and has an inlet opening at the bottom and an outlet opening designed as a pressure port at the top.
  • the housing wall In order to divert the essentially radial flow coming from the impeller into an essentially axially parallel one leading to the pressure port, the housing wall has a bulge. This bulge forms a kind of stowage zone.
  • the efficiency is also comparatively poor there, because the flow between the deflection point in the region of the bulge and the pressure port is only due to the between the Outside of the engine and the inner wall of the unit housing is formed channel where turbulence occurs due to construction.
  • the invention has for its object to provide a generic submersible pump unit with better efficiency, while keeping the slimest possible design.
  • This object is achieved according to the invention in that the pressure-side flow between the bulge and the pressure port is guided through a pipe arranged within the unit housing.
  • a pipe which can be integrated into the housing with little effort in terms of production technology, leads the flow on all sides and in the shortest possible way to the pressure port. It has been shown that the pressure losses which otherwise occur in this area can be reduced considerably by such a tube. In addition, a comparatively slim-line unit with a large free delivery cross section is created.
  • this peripheral component on the housing wall is in the range of two to five times the nozzle speed of the respective unit.
  • the transition from the storage zone to the concentric housing should be rounded, with a transition radius r ü .
  • the unit can be built in a slimmer form, which increases the area of application and reduces the cost of materials.
  • a simple solution consists in providing openings at the beginning and end of the pipe that lies within the unit housing and runs between the storage zone and the pressure connection. Through the openings at different pressure levels, a partial flow for motor cooling is passed through the annular space between the unit housing and the encapsulated stator.
  • the unit is advantageously equipped with a single-bladed, ducted or free-flow impeller, the wall surrounding the impeller then expediently being part of a shell-shaped housing part which belongs to the unit housing and for example forms the lower part of the housing.
  • a shell-shaped housing part can be formed inexpensively from cold-formed steel sheet, which also has the advantage that the roughness of the surface is very low, which in turn benefits the improvement in efficiency.
  • the bulge forming the storage zone in the housing wall is advantageously designed such that the cross section of this bulge follows an arc in the storage area, the diameter this circle corresponds to that of the inlet opening and that of the pipe and the pressure nozzle. This largely ensures that everything that can enter the unit through the inlet opening is also conveyed out again, in particular does not become lodged within the unit.
  • the bulge which forms the storage zone is advantageously arranged in the housing wall in such a way that, viewed in the direction of flow, it connects approximately tangentially to the concentric part of the housing wall.
  • the transition radius from the storage zone to the concentric part of the housing has also proven to be influential. This transition radius r ü should be between the limits d / 8 ⁇ r ü ⁇ d / 4 move.
  • FIG. 1 shows a submersible pump unit which has an encapsulated motor 1 which is seated within the essentially cylindrical unit housing 2.
  • the electrical supply line 3 of the motor 1 is led out of the motor housing 4 and the unit housing 2 upwards.
  • the motor housing 4 sits slightly eccentrically within the unit housing 2, an annular space 5 being formed in this area between the outer circumference of the motor housing 4 and the inside of the unit housing 2. This annular space is closed at the top by the end wall 6 of the unit housing and at the bottom by an annular end wall 7, which forms part of the actual pump housing.
  • the shaft 8 of the motor 1 is led out of the motor housing 4 downwards and sealed against it in this area.
  • the lower free shaft end protrudes into the pump chamber 9 and carries there an impeller 10 in the form of a free-flow impeller.
  • the impeller is closed at the top by a disk-shaped impeller part 11, which is arranged perpendicular to the shaft 8 and carries impeller blades 12.
  • the pump chamber 9 is delimited at the top by the lower end of the motor housing 4 and the end wall 7.
  • the lateral and lower boundary is formed by a molded part 13, which is approximately bowl-shaped, consists of cold-formed sheet metal and is firmly connected to the other unit housing 2, in particular the foot 14.
  • the foot 14 is flush with the cylindrical outer contour of the other unit housing 2 and (not shown) has sufficiently large recesses for the free passage of the medium.
  • the molded part 13 has a circular recess 15 in the area under the impeller 10, that is, in the extension of the shaft 8, which forms the inlet opening of the pump.
  • the outlet opening of the unit is formed by a pressure nozzle 16 arranged on the upper end face, which is connected to the pump chamber 9 via a pipe 17 arranged in the annular space 5 of the unit housing 2, approximately parallel to the longitudinal axis of the unit and the shaft 8.
  • the tube 17 opens into the end wall 7, in the region above a bulge 18 forming a storage zone in the molded part 13.
  • the tube 17 connects to the pump chamber 9 approximately at the level of the disk-shaped impeller part 11.
  • the tube 17 Shortly above its connection to the pump chamber 9, but above the end wall 7, that is to say already in the region of the annular chamber 5, the tube 17 has recesses 19 in the form of circular openings. Corresponding recesses 20 are close the upper end, that is, close to the pressure connection 16 in the pipe 17. These recesses 19 and 20 are at different pressure levels during operation of the pump, so that in addition to the main flow flowing through the pipe 17, a secondary flow flowing out of the pipe 17 via the recesses 19 and re-entering via the recesses 20 adjusts the annular space 5 flows through and thus cools the engine 1. This cooling flow can be adjusted by appropriate dimensioning of the recesses 19 and 20 and other suitable fluidic measures within the annular space 5 according to the cooling requirements.
  • the molded part 13 is shown in detail with reference to FIGS. 2 to 4.
  • the area of the actual pump chamber it has an approximately concentric housing wall 21, which merges tangentially into the corresponding wall part of the bulge 18 in the area 22.
  • the area 22 is in plan view (FIG. 2) both tangential to the concentric housing wall part 21 and to that of the bulge 18 which is eccentrically aligned with the pipe 17.
  • the housing wall 21 merges upwards with a small radius into a horizontal part 23 with which it is connected to the rest of the unit housing 2. This horizontal part 23 is followed, as can be seen in FIG. 3 and FIG. 4, by a collar-shaped part 24.
  • the housing wall 21 merges with a large radius into a likewise horizontal, but inwardly running wall part 25, which limits the pump chamber 9 in this area at the bottom.
  • the horizontal wall part 25 runs downward like a shell toward the recess 15, this shell-shaped part is designated by 26.
  • the radius r with which the housing wall 21 merges into the wall part 25 corresponds to the radius r of the bulge 18, which in this area has a spherical surface follows.
  • the radius r is half the diameter d of the inlet opening 15, the pipe 17.
  • This diameter d also corresponds approximately to the distance between the impeller and the underlying housing parts of the molded part 13. In this way, a free passage of the order of one Ball with the aforementioned diameter d guaranteed by the entire pump unit.
  • a projection 28 is formed in the opposite direction, where the tangents of the housing wall parts 21 of the concentric part and the bulge 18 intersect.
  • the geometric relationships of the molded part 13 have already been explained in the introduction, they are shown in detail in FIG. 2.
  • the ball diameter of the largest ball is indicated with d, which can be conveyed through the unit with the flow.
  • D denotes the diameter of the concentric part of the pump housing, that is to say in the concentric region of the housing wall 21.
  • the bulge 18, which follows a spherical surface with the radius r, is arranged such that the center M of this sphere lies on an arc of a diameter B arranged concentrically with the pump impeller 10.
  • transition radius r ü already mentioned at the beginning is one sixth of the ball diameter in the embodiment shown, but it can be between an eighth and a quarter of the ball diameter d d / 4 ⁇ r ü ⁇ d / 8.
  • the ball diameter d not only determines the design of the molded part 13, but in the same way the diameter of the recess 15, that of the tube 17 and that of the adjoining pressure connector 16.
  • the unit When the pump is operating, the unit is partially or completely immersed in the liquid to be pumped.
  • the pumped medium enters the pump chamber 9 through the inlet opening 15 and is set in motion by the impeller 10, namely in the radial and tangential directions. It is then guided through the housing wall 21 and directed over the area 22 to the bulge 18.
  • a storage zone now forms here, the conveying liquid is deflected upwards, where it enters the pipe 17 and finally exits at the pressure connection 16.
  • the partial flow for cooling that is formed has already been described above.

Landscapes

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

Claims (8)

  1. Groupe moto-pompe submersible offrant un passage libre à des corps sphériques allant jusqu'à un diamètre d, constitué pour l'essentiel d'un moteur électrique (1) et d'une pompe centrifuge entraînée par ce dernier, qui sont disposés sur. le même axe, et comportant une ouverture d'entrée (15) et une ouverture de sortie réalisée sous la forme d'un raccord de refoulement (16), ainsi qu'un carter de pompe à peu près concentrique, réalisé sous la forme d'une pièce préformée et ayant un diamètre intérieur D, carter de pompe dont la paroi (21) présente un renflement (18) qui constitue, pour l'écoulement côté refoulement, une zone d'accumulation dans laquelle le fluide est dévié dans une direction sensiblement parallèle à l'axe et, à partir de là, est dirigé vers le raccord de refoulement, caractérisé en ce que l'écoulement côté refoulement est dirigé, entre le renflement (18) et le raccord de refoulement (16), à travers un tube (17) disposé à l'intérieur du carter (2) du groupe.
  2. Groupe moto-pompe submersible selon la revendication 1, caractérisé en ce que, dans le renflement (18), peut être inscrit un cercle, dont le rayon r se situe entre un tiers et deux tiers du diamètre d des corps sphériques, et correspond de préférence à la moitié du diamètre d des corps sphériques, et en ce que le centre M de ce cercle se trouve sur un arc de cercle disposé concentriquement à l'axe de la pompe, et dont le diamètre B se situe dans la plage entre D - d/6 et D + d/4.
  3. Groupe moto-pompe submersible selon la revendication 1 ou 2, caractérisé en ce que le fond du renflement (18) est une partie d'une surface sphérique.
  4. Groupe moto-pompe submersible selon l'une des revendications précédentes, caractérisé en ce que le tube (17) présente au moins deux perçages (19, 20) situés à des niveaux différents du refoulement, pour dériver une partie du liquide transporté en tant que courant de refroidissement pour le moteur (1).
  5. Groupe moto-pompe submersible selon l'une des revendications précédentes, caractérisé en ce que la pompe comporte un rotor (10) à une pale, non engorgeable ou à écoulement libre, et en ce que la paroi (21) entourant le rotor centrifuge (10) constitue une partie d'un élément de carter (13) en forme de coque.
  6. Groupe moto-pompe submersible selon l'une des revendications précédentes, caractérisé en ce que l'élément de carter (13) en forme de coque est réalisé en une tôle d'acier ayant subi un formage à froid.
  7. Groupe moto-pompe submersible selon l'une des revendications précédentes, caractérisé en ce que la paroi de carter (21), dans la région (22) menant à la zone d'accumulation (considérée dans la direction 27 de l'écoulement), s'étend à peu près tangentiellement à sa partie concentrique et au renflement (18) et rejoint la partie concentrique de la paroi de carter, depuis le renflement (18), en s'arrondissant sous un rayon de transition rü, le rayon de transition rü ayant une valeur située entre un huitième et un quart du diamètre d des corps sphériques.
  8. Groupe moto-pompe submersible selon l'une des revendications précédentes, caractérisé en ce que la paroi de carter est revêtue, au moins dans la région de la zone d'accumulation, d'un matériau résistant à l'usure.
EP93118605A 1992-11-20 1993-11-18 Unité de pompe submersible Expired - Lifetime EP0599204B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4239071A DE4239071C2 (de) 1992-11-20 1992-11-20 Tauchpumpenaggregat
DE4239071 1992-11-20

Publications (2)

Publication Number Publication Date
EP0599204A1 EP0599204A1 (fr) 1994-06-01
EP0599204B1 true EP0599204B1 (fr) 1997-01-22

Family

ID=6473286

Family Applications (1)

Application Number Title Priority Date Filing Date
EP93118605A Expired - Lifetime EP0599204B1 (fr) 1992-11-20 1993-11-18 Unité de pompe submersible

Country Status (3)

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EP (1) EP0599204B1 (fr)
DE (2) DE4239071C2 (fr)
ES (1) ES2098634T3 (fr)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4423149C2 (de) * 1994-07-04 1998-01-29 Orpu Gmbh Mehrstufige Freistrompumpe
DE29711534U1 (de) * 1997-03-06 1998-08-27 Elektra Beckum Ag, 49716 Meppen Tauchpumpe
DE29916897U1 (de) 1999-09-24 2000-01-20 Reich KG, Regel- und Sicherheitstechnik, 35713 Eschenburg Tauchpumpe
EP1260714B1 (fr) 2001-05-25 2006-11-29 Grundfos A/S Unité moteur/pompe avec moteur d'entraînement et pompe immersible
DE10301629B4 (de) * 2003-01-17 2013-05-29 Ksb Aktiengesellschaft Freistrompumpe
DE202020104824U1 (de) 2020-08-20 2021-11-26 K.H. Brinkmann GmbH & Co Kommanditgesellschaft Mediumgekühlte Flüssigkeitspumpe

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3029744A (en) * 1957-03-08 1962-04-17 Mc Graw Edison Co Impeller housing
US3135212A (en) * 1962-03-29 1964-06-02 Symington Wayne Corp Submersible pump
FR2169496A5 (fr) * 1972-01-28 1973-09-07 Sodery
US4076450A (en) * 1976-01-14 1978-02-28 United Centrifugal Pumps Double volute pump with replaceable lips
US4076179A (en) * 1976-04-22 1978-02-28 Kabushiki Kaisha Sogo Pump Seisakusho Centrifugal sewage pump
US4134711A (en) * 1976-11-26 1979-01-16 Engineers Sales-Service Co., Inc. Submersible pump apparatus
CH627236A5 (fr) * 1978-02-14 1981-12-31 Martin Staehle
JPS5838396A (ja) * 1981-08-29 1983-03-05 Ebara Corp グラインダ−ポンプ
JPS6140795U (ja) * 1984-08-17 1986-03-14 ソニー株式会社 電子機器の蓋体
DE3929758C2 (de) * 1989-09-07 1994-11-17 Klein Schanzlin & Becker Ag Kreiselpumpengehäuse in Blechbauweise
JPH03175195A (ja) * 1989-09-26 1991-07-30 Ebara Corp 水中ポンプ

Also Published As

Publication number Publication date
DE59305242D1 (de) 1997-03-06
DE4239071C2 (de) 1997-01-30
ES2098634T3 (es) 1997-05-01
DE4239071A1 (de) 1994-05-26
EP0599204A1 (fr) 1994-06-01

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