EP3317544B1 - Freistrompumpe - Google Patents

Freistrompumpe Download PDF

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Publication number
EP3317544B1
EP3317544B1 EP16733062.0A EP16733062A EP3317544B1 EP 3317544 B1 EP3317544 B1 EP 3317544B1 EP 16733062 A EP16733062 A EP 16733062A EP 3317544 B1 EP3317544 B1 EP 3317544B1
Authority
EP
European Patent Office
Prior art keywords
bundles
blades
impeller
pump according
chokable
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP16733062.0A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP3317544A1 (de
Inventor
Alexander Christ
Jochen Fritz
Christoph Jäger
Toni Klemm
Steffen Schmidt
Rolf Witzel
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.)
KSB SE and Co KGaA
Original Assignee
KSB SE and Co KGaA
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 KSB SE and Co KGaA filed Critical KSB SE and Co KGaA
Priority to PL16733062T priority Critical patent/PL3317544T3/pl
Priority to SI201631388T priority patent/SI3317544T1/sl
Priority to HRP20211632TT priority patent/HRP20211632T1/hr
Publication of EP3317544A1 publication Critical patent/EP3317544A1/de
Application granted granted Critical
Publication of EP3317544B1 publication Critical patent/EP3317544B1/de
Active 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
    • F04D29/18—Rotors
    • F04D29/22—Rotors specially for centrifugal pumps
    • F04D29/2238—Special flow patterns
    • F04D29/2244—Free vortex
    • 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
    • F04D29/18—Rotors
    • F04D29/22—Rotors specially for centrifugal pumps
    • F04D29/24—Vanes
    • F04D29/242—Geometry, shape
    • 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
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2240/00—Components
    • F05B2240/20—Rotors
    • F05B2240/30—Characteristics of rotor blades, i.e. of any element transforming dynamic fluid energy to or from rotational energy and being attached to a rotor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2250/00—Geometry
    • F05B2250/10—Geometry two-dimensional
    • F05B2250/15—Geometry two-dimensional spiral
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2260/00—Function
    • F05B2260/60—Fluid transfer
    • F05B2260/63—Preventing clogging or obstruction of flow paths by dirt, dust, or foreign particles

Definitions

  • the invention relates to a vortex pump with an impeller which has blades for conveying media containing solids.
  • Vortex pumps are also referred to as vortex pumps, the delivery rate of which is transferred to the flow medium by a rotating disc with blades, the so-called vortex impeller.
  • Vortex impellers are particularly suitable for pumping media mixed with solid admixtures, such as waste water.
  • the vortex impeller is a radial impeller that has a large passage for the solids contained in the pumped medium and is less prone to failure.
  • WO 2004/065796 A1 describes a free-flow pump for pumping liquids mixed with solid admixtures.
  • the transition from the suction-side housing wall to the wall of the housing space located radially to the impeller takes place continuously.
  • the housing space is designed asymmetrically.
  • a vortex pump is described, the impeller of which consists of a support disc equipped with open blades.
  • the blades have different heights.
  • a housing wall on the suction side is conical.
  • the distance between the casing wall and the leading edges of the higher blades of the impeller decreases with the diameter.
  • a passage with a minimum extension consistently follows a leading edge of a blade of lesser height, which is inclined towards the impeller outlet.
  • a free, unrestricted impeller passage is called a ball passage. It describes the largest permissible diameter of the solids in order to ensure a blockage-free passage. It is given as the diameter of the sphere in millimeters.
  • the ball passage corresponds at most to the nominal width of the suction or discharge nozzle. In order for this maximum possible ball passage to be achieved with conventional vortex pumps, the distance between the vane front and the housing wall on the suction side must also be at least equal to the nominal width of the suction or discharge nozzle inside the housing.
  • the JP-A-2013181459 shows a self-priming centrifugal pump with a pressure- and suction-side cover plate and a radial impeller with long blades and short intermediate blades. Due to the existing free leading edges, these blades are unsuitable as vortex impeller blades.
  • the impeller of the FR-A-1404875 is at least partially covered and designed for a gas-liquid mixture. Because of the free leading edges, their blades are not suitable for conveying media containing solids, the solids of which would get caught on the blade leading edges.
  • the object of the invention is to provide a free-flow pump that can convey media with larger solids and has the highest possible degree of efficiency in accordance with the design.
  • the free-flow pump should be distinguished by a method of manufacture that is as cost-effective as possible and should ensure a long service life.
  • the vortex pump should be used as widely as possible and be less susceptible to failure, as well as have a favorable NPSH value. Cavitation damage should be avoided.
  • the blades are arranged in bundles on the vortex impeller.
  • the distance between the blades within the bundle is smaller than the distance between the bundles.
  • the construction according to the invention ensures sufficient ball passage with a high delivery efficiency of the pump.
  • the arrangement of the blades in bundles on the support disk makes it possible to reduce the distance between the housing wall on the inlet side and the blade front, while still ensuring sufficient ball passage.
  • the distances between the bundles are greater than the distances between the blades in the bundle, a sufficiently large ball passage is guaranteed even if the distance between the blade front of the impeller is smaller than the inside diameter of the suction nozzle or the pressure nozzle. This avoids blockages and at the same time achieves a high level of efficiency in conveying.
  • the bundled arrangement of the blades makes it possible to reduce the distance between the impeller and the casing wall on the suction side without clogging. This increases the efficiency of the vortex pump.
  • the distance between the blade front of the impeller is preferably less than 90%, in particular less than 80%, of the diameter of the suction mouth or the inner diameter of the suction nozzle.
  • Each bundle includes at least two blades. Bundles with two or three blades each have proven to be particularly advantageous. In a variant of the invention, each bundle comprises four blades.
  • the support disk of the vortex impeller has a hub projection on the suction side on which the blades engage.
  • the blades protrude from the support disk in the suction-side direction and have a course that is curved against the direction of rotation. All the blades can have the same curvature. In an alternative variant, the blades have different curvatures. For example, blades with different curvatures can be arranged within a bundle.
  • the distance between the blades in the bundles is expediently less than 90%, preferably less than 80%, in particular less than 70%, of the distance between the bundles.
  • the vortex impeller comprises two bundles of blades, which are preferably arranged offset from one another by 180 °. It proves to be advantageous if each bundle comprises the same number of blades.
  • the distances between the blades within the bundles and / or the distances between the bundles are specified as the angle of the blade pitch. According to the invention, the angles of the blade division within the bundles are smaller than the angles of the blade division between the bundles.
  • angles of the blade division between the bundles are expediently more than 60 °, preferably more than 70 °, in particular more than 80 °.
  • angle of the blade division within the bundle is less than 70 °, preferably less than 60 °, in particular less than 50 °.
  • the impeller is designed in one piece with the blades. It proves to be advantageous if the impeller and / or the blades are made of a metallic material. A cast material is preferably used.
  • angles of the blade division between the bundles are not an integral multiple of the angle of the blade division within the bundle, so that the arrangement in bundles is not due to an impeller with blades of the same angular division, in which individual blades are omitted.
  • the height of the blades decreases in the radial direction in relation to a reference plane.
  • the decrease is preferably carried out with a bevel angle of more than 2 °, in particular more than 3 °. It has proven to be favorable if the height of the blades decreases with a bevel angle of less than 8 °, in particular less than 7 °.
  • a free-flow pump is shown, in the housing 1 of which an impeller 2 is positioned.
  • the impeller 2 is non-rotatably connected to a shaft, which in Figure 1 is not shown.
  • a hub body 4 which has a bore 5 for screwing in a screw, is used to fasten the impeller 2.
  • the impeller 2 is designed as a vortex impeller.
  • a plurality of blades 7 are arranged on a support disk 6 of the impeller 2.
  • a blade-free space 9 is formed between the impeller 2 and the housing wall 8 on the inlet side.
  • the suction mouth 10 is formed by a housing part 11 on the suction side.
  • the suction mouth 10 forms an inlet for the solid-containing medium and has a diameter D.
  • the suction-side housing part 11 is designed as a suction cover.
  • the impeller 2 is arranged in a pump housing 15.
  • the front side of the vortex impeller 2 is at a distance A from the inside of the suction-side housing part 11 on its outer edge.
  • the distance A is preferably defined as the distance that a normal, which is perpendicular to the housing wall 8 on the suction side, has to the outer edge of the blade front of the impeller 2.
  • the distance A is smaller than the diameter D.
  • the height h of the blades 7 decreases in the radial direction, so that the blade front has a slightly inclined or conical shape
  • Figure 2 shows a perspective view of the impeller 2, which is designed as a vortex impeller.
  • the impeller 2 is an open radial impeller that does not have a cover plate.
  • Each bundle 12 comprises two blades 7 each.
  • the two bundles 12 are arranged on the hub body 4 of the impeller 2, offset from one another by 180 °.
  • FIG. 11 shows a top view of the impeller 2 according to the illustration in FIG Figure 2 .
  • the distance 13 between the bundles has an angle of the blade division of 120 °.
  • the spacing 14 of the blades 7 within the bundle 12 has an angle of the blade pitch of 60 °.
  • the angle of the blade division between the bundles 12 are thus greater by a factor of 2 than the angle of the blade division within the bundle.
  • the angles of the blade division between the bundles 12 are an integral multiple of the angle of the blade division within the bundles 12.
  • Figure 4 shows a perspective illustration of an impeller 2, in which two bundles 12 of blades 7 are arranged on a support disk 6, each bundle 12 each comprising three blades 7. The two bundles are arranged offset from one another by 180 ° on the hub body 4 of the impeller 2.
  • FIG. 11 shows a top view of the impeller 2 according to the illustration in FIG Figure 4 .
  • the distance 13 between the bundles 12 has an angle of the blade division of 84 °.
  • the spacing 14 of the blades 7 within the bundle 12 has an angle of the blade pitch of 48 °.
  • the angles of the blade division between the bundles are thus greater by a factor of 1.75 than the angle of the blade division within the bundle 12.
  • the angles of the blade division between the bundles 12 are therefore not an integral multiple of the angle of the blade division within the bundles 12.
  • Figure 6 shows a view of the vortex pump, in which an impeller 2 is arranged in the pump housing part 15.
  • the housing is a spiral housing.
  • the medium containing solids leaves the vortex pump through a pressure port 17.
  • FIG. 7 shows the impeller 2 as shown in FIG Figure 6 with a section line AA.
  • a section along this line AA is shown.
  • the height h of the blades 7 decreases in the radial direction, that is to say towards the outer diameter of the impeller.
  • the decrease is in relation to a reference plane 16, which in Figure 8 is partially shown in dashed lines.
  • the decrease takes place with a bevel angle ⁇ of 5 °.
  • Figure 8 shows a ball 18 in an upper and a lower position.
  • the ball 18 has a diameter d and a radius a. According to the lower position of the ball 18, the ball 18 plunges into the spaces of the impeller 2 between the bundles 12 by a depth b. This immersed segment of the sphere has a secant c.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Geometry (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
EP16733062.0A 2015-06-30 2016-06-27 Freistrompumpe Active EP3317544B1 (de)

Priority Applications (3)

Application Number Priority Date Filing Date Title
PL16733062T PL3317544T3 (pl) 2015-06-30 2016-06-27 Pompa o swobodnym przepływie
SI201631388T SI3317544T1 (sl) 2015-06-30 2016-06-27 Vrtinčna črpalka
HRP20211632TT HRP20211632T1 (hr) 2015-06-30 2016-06-27 Vrtložna pumpa

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102015212203.4A DE102015212203A1 (de) 2015-06-30 2015-06-30 Freistrompumpe
PCT/EP2016/064855 WO2017001340A1 (de) 2015-06-30 2016-06-27 Freistrompumpe

Publications (2)

Publication Number Publication Date
EP3317544A1 EP3317544A1 (de) 2018-05-09
EP3317544B1 true EP3317544B1 (de) 2021-08-11

Family

ID=56289494

Family Applications (1)

Application Number Title Priority Date Filing Date
EP16733062.0A Active EP3317544B1 (de) 2015-06-30 2016-06-27 Freistrompumpe

Country Status (17)

Country Link
US (1) US10738792B2 (pl)
EP (1) EP3317544B1 (pl)
CN (1) CN107810331B (pl)
AU (1) AU2016288451B2 (pl)
BR (1) BR112017027545B1 (pl)
CA (1) CA2990990C (pl)
DE (1) DE102015212203A1 (pl)
DK (1) DK3317544T3 (pl)
ES (1) ES2896450T3 (pl)
HR (1) HRP20211632T1 (pl)
HU (1) HUE056972T2 (pl)
PL (1) PL3317544T3 (pl)
PT (1) PT3317544T (pl)
RU (1) RU2705785C2 (pl)
SA (1) SA517390579B1 (pl)
SI (1) SI3317544T1 (pl)
WO (1) WO2017001340A1 (pl)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
RU197931U1 (ru) * 2019-11-11 2020-06-05 Общество с ограниченной ответственностью "НПО АкваБиоМ" Свободновихревой погружной насос
DE102020003847A1 (de) 2020-06-26 2021-12-30 KSB SE & Co. KGaA Kreiselpumpe zur Förderung feststoffhaltiger Medien
DE102021110936A1 (de) 2021-04-28 2022-11-03 Herborner Pumpentechnik Gmbh & Co Kg Pumpenlaufrad, Gehäuseelement und Pumpe hiermit
DE102021118384A1 (de) 2021-07-15 2023-01-19 KSB SE & Co. KGaA Leichtbau-Hydraulikdesign für verbesserte 3D-Druckbarkeit
DE102021118564A1 (de) 2021-07-19 2023-01-19 KSB SE & Co. KGaA Schaufelanordnung mit Mikroschaufeln

Family Cites Families (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT83294B (de) * 1917-08-20 1921-03-25 Siemens Schuckertwerke Gmbh Laufrad für Schleuderpumpen.
DE470221C (de) * 1926-10-29 1929-01-08 Karl Plischke Laufrad fuer Kreiselpumpen, insbesondere zur Foerderung von Fluessigkeiten mit groben und faserigen Beimengungen
DE943803C (de) * 1952-10-23 1956-06-01 Philipp Hilge Fa Fluegelradpumpe mit seitlichem Ringkanal
FR1404875A (fr) * 1964-08-10 1965-07-02 Thompson Ramo Wooldridge Inc Turbine centrifuge et procédé de fabrication d'une telle turbine
US4076179A (en) * 1976-04-22 1978-02-28 Kabushiki Kaisha Sogo Pump Seisakusho Centrifugal sewage pump
FR2459892A1 (fr) * 1979-06-22 1981-01-16 Klein Schanzlin & Becker Ag Roue a ailettes a un flasque pour pompes centrifuges
JPS59165891A (ja) * 1983-03-10 1984-09-19 Ebara Corp 渦流ポンプ
SU1236175A1 (ru) * 1984-08-15 1986-06-07 Сумский Филиал Харьковского Ордена Ленина Политехнического Института Им.В.И.Ленина Свободновихревой насос
DE3811990A1 (de) * 1987-04-10 1988-10-20 Speck Pumpenfabrik Walter Spec Peripheralpumpe
RU2020286C1 (ru) * 1992-01-09 1994-09-30 Донат Васильевич Гроховский Способ управления лопастными частотами воздействия в центробежных гидромашинах
JP2002138991A (ja) * 2000-11-06 2002-05-17 Ebara Corp 両吸込渦巻ポンプ
US6514036B2 (en) * 2001-04-27 2003-02-04 Black & Decker Inc. Radial flow fan with impeller having blade configuration for noise reduction
RU26610U1 (ru) * 2002-07-25 2002-12-10 Государственное Унитарное Предприятие "Водоканал Санкт-Петербурга" Незасоряющийся насос
DE10301630A1 (de) 2003-01-17 2004-07-29 Ksb Aktiengesellschaft Freistrompumpe
DE10301629B4 (de) 2003-01-17 2013-05-29 Ksb Aktiengesellschaft Freistrompumpe
US8511998B2 (en) * 2008-05-27 2013-08-20 Weir Minerals Australia Ltd. Slurry pump impeller
JP6022779B2 (ja) * 2012-03-01 2016-11-09 株式会社横田製作所 自吸式遠心ポンプ装置
JP6091308B2 (ja) * 2013-04-17 2017-03-08 株式会社不二工機 排水ポンプ

Also Published As

Publication number Publication date
BR112017027545B1 (pt) 2022-11-16
CN107810331B (zh) 2020-02-21
CA2990990C (en) 2023-10-10
CN107810331A (zh) 2018-03-16
SA517390579B1 (ar) 2021-04-01
ES2896450T3 (es) 2022-02-24
DE102015212203A1 (de) 2017-01-05
AU2016288451B2 (en) 2020-05-14
US10738792B2 (en) 2020-08-11
US20180187692A1 (en) 2018-07-05
BR112017027545A2 (pl) 2018-08-21
RU2705785C2 (ru) 2019-11-11
HUE056972T2 (hu) 2022-04-28
AU2016288451A1 (en) 2018-01-04
CA2990990A1 (en) 2017-01-05
SI3317544T1 (sl) 2022-01-31
EP3317544A1 (de) 2018-05-09
RU2018103265A3 (pl) 2019-09-04
DK3317544T3 (da) 2021-11-01
PT3317544T (pt) 2021-11-12
PL3317544T3 (pl) 2021-12-27
RU2018103265A (ru) 2019-07-31
HRP20211632T1 (hr) 2022-01-21
WO2017001340A1 (de) 2017-01-05

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