EP3224481A1 - Pompe centrifuge à rotor radial à déversement axial - Google Patents

Pompe centrifuge à rotor radial à déversement axial

Info

Publication number
EP3224481A1
EP3224481A1 EP15798457.6A EP15798457A EP3224481A1 EP 3224481 A1 EP3224481 A1 EP 3224481A1 EP 15798457 A EP15798457 A EP 15798457A EP 3224481 A1 EP3224481 A1 EP 3224481A1
Authority
EP
European Patent Office
Prior art keywords
impeller
centrifugal pump
less
pump according
ratio
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.)
Withdrawn
Application number
EP15798457.6A
Other languages
German (de)
English (en)
Inventor
Björn WILL
Annika FLEDER
Harald ROKLAWSKI
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 AG
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 AG filed Critical KSB AG
Publication of EP3224481A1 publication Critical patent/EP3224481A1/fr
Withdrawn legal-status Critical Current

Links

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
    • F04D29/40—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
    • F04D29/448—Fluid-guiding means, e.g. diffusers especially adapted for liquid pumps bladed diffusers
    • 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
    • F04D29/2205—Conventional flow pattern
    • F04D29/2216—Shape, geometry
    • 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
    • F04D1/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D1/06—Multi-stage 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
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/52—Casings; Connections of working fluid for axial pumps
    • F04D29/54—Fluid-guiding means, e.g. diffusers
    • F04D29/548—Specially 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
    • F05D2250/00—Geometry
    • F05D2250/70—Shape
    • F05D2250/71—Shape curved

Definitions

  • the invention relates to a centrifugal pump according to the preamble of claim 1.
  • the centrifugal pump has at least one radially formed impeller, which is arranged downstream of a guide.
  • kinetic energy is converted into pressure energy.
  • a diversion of the medium takes place.
  • the swirl is often reduced for inflow to a next stage.
  • a centrifugal pump is described one or more stages with at least one impeller.
  • the impeller is downstream of a stator in the flow direction.
  • the stator has a plurality of guide vanes, which form in the direction of an outlet opening pointing Leitradkanäle.
  • DE 19822 223 A1 describes a multi-stage centrifugal pump.
  • impellers are arranged to rotate.
  • the pumped medium flows to a first impeller.
  • Downstream of the impeller is a Leitradteil with the kinetic energy is converted into pressure energy.
  • the Leitradteil deflects the fluid in its flow direction.
  • DE 33 15 350 C2 relates to a stator for centrifugal pumps with diffuser-shaped expanded guide channels.
  • the outer radial Leitkanalbegrenzung is formed by a housing receiving the stator.
  • the object of the invention is to provide a centrifugal pump with the smallest possible radial space.
  • the centrifugal pump should be characterized by the highest possible efficiency, a cost-effective design and reliable operation. Furthermore, the longest possible lifetime should be guaranteed.
  • the centrifugal pump has a radially formed impeller, which, however, is designed to be distributed axially. While in conventional radial wheels, the flow distribution takes place in the radial direction, the tuning in the impeller according to the invention is directed axially. This results in an S-beat in the meridian section of the impeller. In the Zwitterlaufrad invention, the flow exits axially from the impeller. The flow is then decelerated in a single stator component, deflected and the swirl reduced for inflow to the next stage.
  • the fluid emerging from the impeller is initially decelerated in a downstream guide device and then fed in an overflow geometry to the subsequent return section.
  • the ratio of the stepped inner diameter to the outer diameter at the impeller outlet is less than 1.3, preferably less than 1.2, in particular less than 1.1.
  • the step diameter in relation to the impeller diameter at the impeller outlet is often more than 1.5 times larger. This leads to a high radial construction cost.
  • the stage diameter is significantly reduced, thus saving material.
  • the blade outlet angle of the impeller is less than 50 °, preferably less than 40 °, in particular less than 30 °.
  • the blade exit angle is characteristic of the energy conversion.
  • the blade thickness is preferably more than 2 mm, in particular more than 4 mm. Furthermore, it proves to be advantageous if the blade thickness is less than 10 mm, in particular less than 7 mm.
  • the riq value of such pumps is preferably £ 50.
  • the specific speed n q is given as a dimensionless value and is defined as > where n is the
  • the ratio of the outer diameter at the impeller outlet to the inner diameter at the impeller outlet is more than 1, 0 and in particular more than 1, 1.
  • a relevant geometric relationship of the present invention is also the ratio of the outer diameter of the impeller outlet with respect to the outer diameter at the suction mouth. In a favorable variant, this is more than 1.4, preferably more than 1.5, and in particular more than 1.6.
  • Another characteristic feature of the centrifugal pump according to the invention is the ratio of the axial position of the outer diameter of the impeller outlet to the axial position of the inner diameter of the impeller outlet. This is preferably less than 1, 1 and greater than 0.9. In a favorable embodiment of the invention, this ratio is less than 1.05 and greater than 0.95, in particular less than 1.01 and greater than 0.99.
  • a ratio for the Leitradeinlinger can be defined.
  • the axial position of the outer diameter at the Leitradeinstory to the axial position of the inner diameter at the Leitradeinstory is preferably less than 1, 1 and greater than 0.9. In a favorable embodiment of the invention, this ratio is preferably less than 1.05 and greater than 0.95, in particular less than 1.01 and greater than 0.99.
  • the angle v La is greater than 40 °, preferably greater than 50 °, in particular greater than 60 °.
  • the number of blades of the stator is more than 4, preferably more than 6.
  • the trailing edge of the stator is rounded, preferably with a ratio of the radius of the trailing edge to the thickness of the blade of less than 1.0, in particular less than 0.9.
  • the diffuser can be designed with or without "Intersplif'-Vanes.
  • the impeller has a cover plate.
  • the impeller is a closed impeller, in which the fluid enters in the axial direction, is then transferred radially and finally, due to the S-shaped meridian, is released axially.
  • the impeller has a support disk.
  • the support plate is at least partially turned off. By twisting off the outer region of the support disk, an axial distribution is made possible. The result is an S-shaped meridian section. The design leads to a reduced step diameter. This saves material.
  • a space is present between the impeller and the guide.
  • this is a Radcostraum.
  • the guide is preferably fixedly connected to the pump housing. It can be formed by the step housing itself.
  • FIG. 1 shows a schematic axial section drawing through a centrifugal pump stage
  • FIG. 2 is a sectional view of an impeller and a stator
  • FIG. 3 is a perspective view of an impeller and a stator
  • Figure 4 is a representation of the blade outlet angle
  • FIG. 5 shows a meridian section
  • FIG. 6 shows the angles in the meridian
  • FIG. 7 shows a representation of the blades on the cover disk of the impeller
  • 8 shows a representation of the blades on the cover plate of the stator.
  • FIG. 1 shows a schematic axial section through a centrifugal pump stage.
  • an impeller 1 is arranged on a shaft 2.
  • a housing 3 surrounds the impeller 1.
  • a fluid flows in the axial direction into the impeller 1, is then deflected in a radial direction and leaves the impeller 1 again in the axial direction.
  • the fluid then flows into a guide 4, which is formed in the embodiment as a stator and the step housing 3 is formed.
  • Figure 2 shows an impeller 1 having a cover plate 5 and a support plate 6.
  • the support plate 6 is turned off in its outer region.
  • the cover plate 5 extends in the radial direction further than the support plate 6.
  • an axially distributing impeller 1 is created, which is designed as a Zwitterlaufrad.
  • the Zwitterlaufrad is a radial wheel, in which the outflow is directed axially. This is made possible by the turning of the support plate 6 in its outer region.
  • FIG. 3 shows a perspective view of the impeller 1, which is arranged on a shaft 2.
  • the conveying medium flows from the impeller 1 into the guide device 4.
  • the guide device 4 comprises guide vanes 7.
  • Guide vanes 8 are formed between adjacent guide vanes 7.
  • guide elements 9 can be arranged, which are also called inter-split vanes. These are designed as blades. They have a curvature for deflecting the flow.
  • the guide elements 9 protrude at least partially into the guide channels 8. They extend from the exit of the guide channels 8 along their curvature increasingly in the axial direction.
  • FIG. 5 shows a meridian section of the hydraulic according to the invention.
  • the internal step diameter D S ti in this example corresponds approximately to the outside diameter at the impeller outlet D 12a .
  • a relevant geometric ratio is on the one hand the relative outside diameter Di2a at the impeller outlet, based on the outside diameter D 11a at the suction mouth. This ratio is preferably greater than 1.4, in particular greater than 1.6.
  • the ratio of the outer diameter at the impeller outlet D 12a to the inner diameter at the impeller outlet D 12 j should be (alternatively
  • a characteristic feature of the hybrid hydraulic system according to the invention is, in contrast to semi-axial machines, the ratio of the axial position Xi2a of the outer diameter at the impeller outlet to the axial position xi 2i of the inner diameter at the impeller outlet. This is
  • Figure 6 shows the angles in the meridian Yu and Yu.
  • the angle is Y La £ 60 °.
  • the angle Y Le is also £ 60 °.
  • FIG. 7 shows an illustration of the vanes on the cover disk of the impeller for the sake of clarity.
  • Figure 8 shows a representation of the blades for clarity on cover plate from the stator.

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)

Abstract

L'invention concerne une pompe centrifuge comportant au moins un rotor (1) de conception radiale. Le rotor (1) est conçu pour un déversement axial. Un dispositif de guidage (4) est agencé en aval du rotor (1).
EP15798457.6A 2014-11-25 2015-11-24 Pompe centrifuge à rotor radial à déversement axial Withdrawn EP3224481A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102014223942.7A DE102014223942A1 (de) 2014-11-25 2014-11-25 Kreiselpumpe mit einer Leiteinrichtung
PCT/EP2015/077513 WO2016083381A1 (fr) 2014-11-25 2015-11-24 Pompe centrifuge à rotor radial à déversement axial

Publications (1)

Publication Number Publication Date
EP3224481A1 true EP3224481A1 (fr) 2017-10-04

Family

ID=54697584

Family Applications (2)

Application Number Title Priority Date Filing Date
EP15798458.4A Active EP3224483B1 (fr) 2014-11-25 2015-11-24 Pompe centrifuge avec dispositif de guidage
EP15798457.6A Withdrawn EP3224481A1 (fr) 2014-11-25 2015-11-24 Pompe centrifuge à rotor radial à déversement axial

Family Applications Before (1)

Application Number Title Priority Date Filing Date
EP15798458.4A Active EP3224483B1 (fr) 2014-11-25 2015-11-24 Pompe centrifuge avec dispositif de guidage

Country Status (4)

Country Link
EP (2) EP3224483B1 (fr)
DE (1) DE102014223942A1 (fr)
DK (1) DK3224483T3 (fr)
WO (2) WO2016083382A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
RU2735978C1 (ru) * 2020-06-24 2020-11-11 Игорь Олегович Стасюк Ступень многоступенчатого лопастного насоса
RU2754049C1 (ru) * 2020-12-12 2021-08-25 Игорь Олегович Стасюк Ступень лопастного многоступенчатого насоса

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN108953158B (zh) * 2018-09-20 2024-07-12 南元泵业有限公司 多出口离心泵
CN113074138B (zh) * 2020-01-06 2022-05-17 广东威灵电机制造有限公司 扩压装置、风机及吸尘器
DE102020133459A1 (de) 2020-12-15 2022-06-15 KSB SE & Co. KGaA Herstellung eines Diffusors als Gruppe von Kanälen
RU206628U1 (ru) * 2021-03-06 2021-09-17 Игорь Олегович Стасюк Ступень лопастного многоступенчатого насоса диагонально-овального типа

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1771711A (en) * 1928-01-19 1930-07-29 Voith Gmbh J M Split guide blade for centrifugal pumps
GB489318A (en) * 1937-07-30 1938-07-25 Cebert Boardman Improvements in centrifugal pumps and motors
US2857849A (en) * 1953-11-13 1958-10-28 Joseph R Smylie Motor driven pumping units
US3398694A (en) * 1966-08-11 1968-08-27 Marine Constr & Design Co Submersible pump device for net brailing
DE3315350C2 (de) 1983-04-28 1985-10-03 Klein, Schanzlin & Becker Ag, 6710 Frankenthal Leitrad für Kreiselpumpen
JPH01318790A (ja) * 1988-06-17 1989-12-25 Hitachi Ltd 多段ポンプの水返し羽根
DE3912279A1 (de) 1989-04-14 1990-10-18 Klein Schanzlin & Becker Ag Leitrad fuer kreiselpumpen
DE3943273C2 (de) * 1989-12-29 1996-07-18 Klaus Union Armaturen Horizontal angeordnete Kreiselpumpe mit Spaltrohrmagnetkupplung
JPH11173296A (ja) * 1997-12-11 1999-06-29 Ebara Corp ポンプのディフューザ装置
DE19822223C5 (de) 1998-05-18 2005-09-15 Kaefer Isoliertechnik Gmbh & Co Kg Betonfräse zum Fräsen von, insbesondere beschichteten, Beton- oder Estrichböden
NL1009759C2 (nl) * 1998-07-28 2000-02-01 Vogel Willi Ag Rotatie-inrichting.
CN103591051A (zh) * 2013-11-07 2014-02-19 江苏大学 一种具有副叶片的空间导叶

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
RU2735978C1 (ru) * 2020-06-24 2020-11-11 Игорь Олегович Стасюк Ступень многоступенчатого лопастного насоса
RU2754049C1 (ru) * 2020-12-12 2021-08-25 Игорь Олегович Стасюк Ступень лопастного многоступенчатого насоса

Also Published As

Publication number Publication date
EP3224483A1 (fr) 2017-10-04
WO2016083382A1 (fr) 2016-06-02
DK3224483T3 (da) 2021-12-06
WO2016083381A1 (fr) 2016-06-02
DE102014223942A1 (de) 2016-06-30
EP3224483B1 (fr) 2021-09-29

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