EP3224483A1 - Pompe centrifuge à dispositif directeur - Google Patents

Pompe centrifuge à dispositif directeur

Info

Publication number
EP3224483A1
EP3224483A1 EP15798458.4A EP15798458A EP3224483A1 EP 3224483 A1 EP3224483 A1 EP 3224483A1 EP 15798458 A EP15798458 A EP 15798458A EP 3224483 A1 EP3224483 A1 EP 3224483A1
Authority
EP
European Patent Office
Prior art keywords
guide
impeller
centrifugal pump
pump 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.)
Granted
Application number
EP15798458.4A
Other languages
German (de)
English (en)
Other versions
EP3224483B1 (fr
Inventor
Annika FLEDER
Björn WILL
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 EP3224483A1 publication Critical patent/EP3224483A1/fr
Application granted granted Critical
Publication of EP3224483B1 publication Critical patent/EP3224483B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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 impeller, which is followed by a guide.
  • the guide comprises guide vanes. Between the vanes guide channels for the fluid to be formed.
  • Such guide devices can be designed as guide wheels. From the impeller exiting fluid enters the guide. In the guide kinetic energy is converted into pressure energy. Furthermore, 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.
  • DE 1 98 22 223 A1 describes a multi-stage centrifugal pump.
  • impellers are arranged to rotate.
  • the fluid flows to a first impeller and thereby experiences an increase in pressure.
  • a stator part Downstream of the impeller, a stator part is converted with the speed energy into pressure energy.
  • the Leitradteil also 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.
  • stages of ultrahigh-pressure centrifugal pumps have very large step diameters relative to the impeller outer diameter. Frequently, the internal step diameter is more than a factor of 1.5 greater than the impeller diameter.
  • the delay of the flow takes place in a Leitraddiffusor.
  • the reduction of the peripheral speed component occurs in a return blading.
  • the object of the invention is to provide a centrifugal pump with the smallest possible radial space.
  • the centrifugal pump should have the highest possible efficiency. A flow separation should be largely prevented. Furthermore, a loss with as little loss as possible should be ensured.
  • the centrifugal pump should be characterized by the most cost-effective construction and reliable operation. Furthermore, the longest possible lifetime should be guaranteed.
  • additional guide elements are arranged at the outlet of at least part of the guide channels.
  • the guide elements noticeably increase the step efficiency.
  • the guide elements open up new freedoms in the design of the guide. So it is possible, for example, that the vanes must be less curved at the outlet.
  • a strong deflection at the diffuser outlet was required. This is because the flow coming from the diffuser in this area is very susceptible to detachment and therefore the flow must not be diverted here. Therefore, in conventional centrifugal pumps, the guide vanes had to be strongly curved in the region of small radii in order nevertheless to realize a deflection. Due to the inventive integration of guide elements at the outlet of the guide channels formed between the guide vanes, such a high curvature of the guide vanes is no longer necessarily required.
  • the guide elements are formed as blades, which protrude at least partially into the guide channels.
  • the guide elements form intermediate cut blades.
  • the guide vanes of the stator extend from an entrance to an exit.
  • the inlet and the outlet of the guide is defined as an entry or exit in the guide channels, which are formed between the guide vanes.
  • the guide elements formed as intermediate cut-off vanes are arranged at the outlet of at least part of the guide channels and preferably project into the guide channels. According to the invention, these intermediate cut blades extend from the outlet of the guide channels in the flow direction to the next stage.
  • the guide elements have a curvature for deflecting the flow.
  • the impeller is designed as a radial wheel. It proves to be particularly advantageous if the impeller is axially distributing. Such wheels are also referred to as hybrid wheels. While in conventional radial impellers, the flow distribution is in the radial direction, the outflow is axially directed at a hybrid impeller. This results in an S-beat in the meridian section of the hybrid impeller.
  • This inventive combination of a hybrid impeller and the integration of guide elements in the subsequent guide brings with it considerable advantages.
  • conventional centrifugal pumps with conventional radially distributing radial impellers the fluid emerging from the impeller is first decelerated in a subsequent stator and then fed in a Kochströmgeometrie the subsequent return section.
  • the stages of ultra-high pressure centrifugal pumps have very large stage diameter based on the impeller outer diameter.
  • the internal step diameter is often greater than 1.5 times larger than the outside diameter of the impeller.
  • the delay in the flow takes place in the diffuser.
  • the reduction of the peripheral speed component is accomplished by the subsequent return blading.
  • the flow exits axially from the impeller.
  • the flow is then decelerated in a single component, diverted, and the swirl reduced for inflow to the next stage.
  • this usually leads to significantly higher losses than conventional hydraulic systems, with a pure radial wheel, but in turn require more space.
  • the inventive combination of a hybrid impeller with a subsequent guide having guide elements allows a compact design of the centrifugal pump with minimum stages diameters and at the same time ensures a low-loss delay and an improvement of the outflow.
  • a centrifugal pump is created, which has a high efficiency despite compact design.
  • the inflow to the next stage is thereby significantly improved.
  • the impeller has a cover plate.
  • the impeller is a closed impeller, in which the fluid enters in the axial direction, is then deflected radially, but finally, due to the S-shaped meridian, is released axially.
  • the impeller has a support plate.
  • the support disk is at least partially off turned. 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 stage diameter. This saves material.
  • a space is present between the impeller and the guide. Preferably, this is a Radateraum.
  • the guide is fixedly connected to the pump housing or can be formed by the stage housing itself.
  • FIG. 1 shows an axial section showing an impeller and a guide
  • FIG. 2 shows a perspective view of the impeller and the guide
  • Figure 3a is a perspective view with streamlines based on a
  • Figure 3b is a perspective view with streamlines based on a
  • 3c shows a perspective view with flow vectors based on a
  • FIG. 4 shows a perspective view of the guide
  • 5a is a perspective view of the guide with flow vectors based on a flow simulation
  • FIG. 5b is a perspective view of the guide device with flow vectors on the basis of a flow simulation
  • Figure 5c is a perspective view of the guide with flow vectors based on a flow simulation.
  • Figure 1 shows an example of a section of a multi-stage centrifugal pump.
  • Pump comprises a plurality of series-connected stages, of which a stage is shown by way of example in FIG.
  • an impeller 1 is arranged on a shaft 2.
  • a step housing 3 surrounds the impeller. 1 A fluid flows in the axial direction in the impeller 1, is then deflected in a radial direction and finally leaves the impeller 1 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.
  • the impeller 1 has 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 also referred to as a hybrid impeller.
  • the name Zwitter- impeller results because it is a radial wheel, but in which the outflow is directed axially. This is made possible by the turning off of the support disk 6 in its outer region.
  • FIG. 1 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 4.
  • the guide 4 includes vanes 7. Between adjacent vanes 7 guide channels 8 are formed.
  • guide elements 9 are arranged at the outlet of the guide channels.
  • FIGS. 3 a, 3 b, 3 c show that the flow separation can be greatly reduced by integration of the guide elements 9 into the guide 4.
  • Figure 4 shows a perspective view of the guide 4. It can be seen that the guide elements 9 are formed as blades. These have a curvature for deflecting the flow. According to the invention, the guide elements project at least partially into the guide channels 8. The guide elements 9 extend starting from the outlet of the guide channels 8 downstream increasingly in the axial direction.
  • Figures 5a, 5b and 5c show flow vectors on three different
  • the guide elements 9 provide for a deflection of the flow in the axial direction.
  • the inventive combination of a hybrid hydraulic system consisting of a rotor 1, which is designed as a hybrid impeller, a guide 4, which is designed as a hybrid stator, and the integration of guide elements 9, which are arranged as intermediate cut blades at Leitradaustritt lead to a centrifugal pump, which has a compact design and thereby has a high stage efficiency.

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 comprenant un rotor (1). Un dispositif directeur (4) est monté en aval du rotor (1). Le dispositif directeur (4) comprend des aubes, entre lesquelles sont formés des canaux directeurs (8). L'invention prévoit de disposer des éléments de guidage (9) au niveau de la sortie d'au moins une partie des canaux directeurs (8).
EP15798458.4A 2014-11-25 2015-11-24 Pompe centrifuge avec dispositif de guidage Active EP3224483B1 (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/EP2015/077514 WO2016083382A1 (fr) 2014-11-25 2015-11-24 Pompe centrifuge à dispositif directeur

Publications (2)

Publication Number Publication Date
EP3224483A1 true EP3224483A1 (fr) 2017-10-04
EP3224483B1 EP3224483B1 (fr) 2021-09-29

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 After (1)

Application Number Title Priority Date Filing Date
EP15798457.6A Withdrawn EP3224481A1 (fr) 2014-11-25 2015-11-24 Pompe centrifuge à rotor radial à déversement axial

Country Status (4)

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

Families Citing this family (6)

* 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
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
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

Also Published As

Publication number Publication date
WO2016083382A1 (fr) 2016-06-02
DK3224483T3 (da) 2021-12-06
EP3224481A1 (fr) 2017-10-04
WO2016083381A1 (fr) 2016-06-02
DE102014223942A1 (de) 2016-06-30
EP3224483B1 (fr) 2021-09-29

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