EP0386010B1 - Kreiselpumpenlaufrad - Google Patents

Kreiselpumpenlaufrad Download PDF

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Publication number
EP0386010B1
EP0386010B1 EP88907657A EP88907657A EP0386010B1 EP 0386010 B1 EP0386010 B1 EP 0386010B1 EP 88907657 A EP88907657 A EP 88907657A EP 88907657 A EP88907657 A EP 88907657A EP 0386010 B1 EP0386010 B1 EP 0386010B1
Authority
EP
European Patent Office
Prior art keywords
impeller
blades
cover disk
blade
centrifugal pump
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
EP88907657A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0386010A1 (de
Inventor
Axel Riel
Rolf Scherer
Jörg STARKE
Renzo Ghiotto
Primo Lovisetto
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 AG
Lowara SRL
Original Assignee
KSB AG
Lowara SRL
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
Family has litigation
First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=6336169&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=EP0386010(B1) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by KSB AG, Lowara SRL filed Critical KSB AG
Priority to AT88907657T priority Critical patent/ATE72883T1/de
Publication of EP0386010A1 publication Critical patent/EP0386010A1/de
Application granted granted Critical
Publication of EP0386010B1 publication Critical patent/EP0386010B1/de
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
    • F04D29/00—Details, component parts, or accessories
    • F04D29/18—Rotors
    • F04D29/22—Rotors specially for centrifugal pumps
    • F04D29/2205—Conventional flow pattern
    • F04D29/2222—Construction and assembly

Definitions

  • the invention relates to a centrifugal pump impeller according to the preamble of the main claim.
  • Centrifugal pump impellers can be manufactured in various ways.
  • closed impellers blades are arranged between two cover disks, which form the impeller channels.
  • These impellers are generally manufactured as cast or sheet metal structures.
  • the cast construction has the disadvantage that impellers with small outlet widths cannot be produced with this method, since there are difficulties with the very narrow cast cores which determine the cross section of the blade channels.
  • GB-PS 537 727 offers a solution to this problem in such a way that a so-called open impeller is created, so to speak, which is converted into a closed impeller with the aid of a cover disk designed as a separate component.
  • a cover plate designed as a casting with cast-on blades is produced, which is possible without the use of complicated parts.
  • the DE-PSen 509 458 and 737 000 show impellers, the vaneless suction-side cover disks of which are in contact with the bladed pressure-side cover disks and are detachably connected to the impeller hubs. These are pumps for use in the field of food technology, which require access to the inside of the impeller and therefore a removable impeller cover plate for better cleaning.
  • GB-PS 728 972 shows a centrifugal pump impeller composed of several thick-walled parts, in which, in order to avoid cavitation damage in the inlet area, the flow-carrying parts are coated with stainless steel or where parts made of stainless steel are used.
  • the suction-side cover plate is formed in two parts, a cylindrical inlet ring forming the suction mouth being welded liquid-tight to a curved impeller cover plate.
  • the blades themselves are continuously welded to the suction and pressure side cover plates.
  • the invention has for its object one for centrifugal pump impellers assembled from individual sheet metal parts Find a construction that is suitable for high speeds (up to approx. 4300 rpm) and is insensitive to static and dynamic loads. This object is achieved in accordance with the characterizing part of the main claim.
  • the solution according to the invention lies in complete contrast to this. It was recognized as essential that a good connection between the blades and the force-introducing cover plate is required.
  • the design according to the invention serves to avoid tension or deformation of the impeller which is responsible for tearing of the individual parts in the area of the connections.
  • the very high loads in the impeller inlet area are reliably absorbed by the very rigid bond between the suction mouth and the blades.
  • the lower load level prevailing in the impeller outlet area is taken into account. Accordingly, the decoupling prevents the different deformations from being transferred to the other part.
  • Embodiments of the invention provide that the blade-less cover plate is welded to the blades.
  • a further embodiment of the invention has proven to be advantageous, according to which welding points for attaching the bladeless cover plate to the blades are arranged at the same distance from the axis of rotation.
  • this solution represents a departure from the usual design principles.
  • a further embodiment of the invention provides that the attachment point for the suction mouth lies on a conical surface whose half cone angle ⁇ formed with the axis of rotation has a value between 40 ° and 65 °, the intersection of the conical surface with the axis of rotation by a on the outside the bladed cover disk from the impeller outer knife is defined on the axis of rotation.
  • Tests have shown that the arrangement of the attachment point between the suction mouth and the blade assembly, which is preferably carried out as a welded connection, produces an extraordinarily high rigidity of the blade assembly in the range specified. Due to the fact that there is no connection between the suction mouth and the vane-free cover plate, a decoupling occurs, which prevents damage to the connection points or welding points.
  • the largest outer diameter of the suction mouth is a maximum of 25 mm larger than the inlet diameter. This measure, which ensures easy deformability of the suction mouth, ensures sufficient coverage of the blade inlet and thus stiffening of the impeller inlet area.
  • a seal is arranged in the overlap area between the bladeless cover disk and the suction mouth. This measure prevents backflows between the impeller channels and the wheel space.
  • Yet another embodiment of the invention provides that one or more sheet metal parts which form the blades are attached to the bladed force-transmitting cover plate.
  • the bladed cover disk which is responsible for the transmission of forces between the drive motor and the liquid to be pumped, has a corresponding connection to the pump shaft. According to the power to be transmitted, the connection points between the force-transmitting cover disk and the blades attached to it are dimensioned accordingly.
  • a further embodiment of the invention provides that the bladed cover plate is provided with beads running between the blades and corresponding to the shape of the blade channel. This measure ensures excellent concentricity of the centrifugal pump impeller.
  • An additional advantage results from the use of blades, the blade root of which is developed in an L-shape relative to the flow-carrying blade surface. It can be fastened between the individual beads, which creates a particularly smooth flow channel if the depth of the bead corresponds to the thickness of the blade root. In the opposite case, when the blade feet are attached directly to the beads, the impeller outlet width is increased.
  • Fig. T shows a cross section through the impeller (1) designed according to the invention.
  • a hub (3) is arranged on a pump shaft (2), by means of which the forces to be transmitted are introduced into a bladed cover disk (4).
  • a plurality of blades (5) are fastened to the bladed cover plate (4) by means of a welded connection. Soldered or adhesive connections are also possible.
  • the use of a wide variety of blade shapes is possible, with the only important thing being that reliable attachment takes place between the blade feet and the force-transmitting cover disk. This can be done in a simple manner, for. B. by means of the number of welded connections, d, he material dimensioning and the shape.
  • a suction mouth (6) designed as a separate component, which covers the inlet area of the blade channels (7) and is attached directly to the blades (5).
  • the attachment here is carried out by a weld seam (8) which, in the area of the largest diameter of the suction mouth (6), creates a connection with the blades (5) or their blade heads.
  • a weld seam (9) can also be arranged directly in the inlet area of the impeller or in between.
  • the shovel-free cover disk (10) lies directly against the shovels (5) or their shovel heads and is connected to them by welding points (11).
  • the welding points (11) are arranged here on a circle, the diameter of which is smaller than the outer diameter of the impeller. A possible reduction in the outer diameter of the impeller in the sense of the known turning does not impair the strength of the construction.
  • the cone (12) is shown in dashed lines, on the imaginary surface of which the connection between the blades (5) and the suction mouth (6) takes place.
  • the half cone angle ( ⁇ ), formed by the axis of rotation and the cone surface, is in the order of 40 ° to 65 °.
  • the intersection of the cone with the axis of rotation is the point at which a solder (13) cut from the outer diameter of the impeller on the outside of the bladed cover disc intersects the axis of rotation.
  • FIG. 2 shows a top view of the bladed cover disk or a view of the rear of the impeller.
  • the beads (14) embossed therein correspond in their course to the course of the blade channel (7).
  • Surfaces (15) remaining between the beads serve to accommodate the blade feet (16), cf. Fig. 1.
  • the depth of the beads (14) corresponds to the material thickness of the blade feet (16), which results in a smooth-surface blade channel.
  • the shovel feet (16) are connected to the bladed cover disc (4) here by means of several welding points (17).

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
EP88907657A 1987-09-17 1988-09-09 Kreiselpumpenlaufrad Expired - Lifetime EP0386010B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT88907657T ATE72883T1 (de) 1987-09-17 1988-09-09 Kreiselpumpenlaufrad.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3731161A DE3731161C2 (de) 1987-09-17 1987-09-17 Kreiselpumpenlaufrad
DE3731161 1987-09-17

Publications (2)

Publication Number Publication Date
EP0386010A1 EP0386010A1 (de) 1990-09-12
EP0386010B1 true EP0386010B1 (de) 1992-02-26

Family

ID=6336169

Family Applications (1)

Application Number Title Priority Date Filing Date
EP88907657A Expired - Lifetime EP0386010B1 (de) 1987-09-17 1988-09-09 Kreiselpumpenlaufrad

Country Status (8)

Country Link
US (1) US5082425A (it)
EP (1) EP0386010B1 (it)
CN (1) CN1015068B (it)
AT (1) ATE72883T1 (it)
CA (1) CA1321103C (it)
DE (2) DE3731161C2 (it)
IN (1) IN169694B (it)
WO (1) WO1989002538A1 (it)

Families Citing this family (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3939156C2 (de) * 1989-11-27 1994-01-27 Grundfos International A S Bje Zusammengesetztes Laufrad für eine Kreiselpumpe
US5336050A (en) * 1993-05-06 1994-08-09 Penn Ventilator Co. Inc. Ventilator fan device
DE4446193C2 (de) * 1994-12-23 1997-01-09 Grundfos As Einbauten für Kreiselpumpen und Verfahren zu deren Herstellung
DE19746850A1 (de) * 1997-10-23 1999-04-29 Wilo Gmbh Laufrad aus Blech
US6447244B1 (en) 1999-05-14 2002-09-10 Argo-Tech Corporation Centrifugal pump apparatus and method for using a single impeller with multiple passes
US6398494B1 (en) 1999-05-14 2002-06-04 Argo-Tech Corporation Centrifugal pump impeller
US6447262B1 (en) 1999-05-14 2002-09-10 Argo-Tech Corporation Pumping system for a multi-stage pump
CA2358722A1 (fr) * 2001-10-11 2003-04-11 Alstom Canada Inc. Turbine hydraulique avec tourbillon centripete et distributeur axial
JP4566741B2 (ja) * 2002-08-28 2010-10-20 株式会社荏原製作所 遠心式羽根車及びポンプ装置
CN1546868A (zh) * 2003-12-04 2004-11-17 北京本然科技有限公司 高势比、内减摩、向心增压离心泵及其技术组合方法与实例
AT506342B1 (de) 2008-01-25 2011-03-15 Bitter Engineering & Systemtechnik Gmbh Laufrad für eine pumpe
JP4561852B2 (ja) 2008-03-26 2010-10-13 株式会社日立プラントテクノロジー 羽根車
US9599120B2 (en) * 2012-08-24 2017-03-21 Asmo Co., Ltd. Impeller for centrifugal pump and centrifugal pump of vehicle washer device
FR3007086B1 (fr) * 2013-06-18 2015-07-03 Cryostar Sas Roue centrifuge
DE102015202417A1 (de) 2015-02-11 2016-08-11 Ksb Aktiengesellschaft Stömungsführendes Bauteil
DE102016217110A1 (de) 2016-09-08 2018-03-08 KSB SE & Co. KGaA Kreiselpumpe
CN109322842B (zh) * 2018-11-26 2024-03-15 昆山佰斯拓机械设备有限公司 带前盖板叶片及槽口的无蜗壳离心通风机及工作方法
DE102022201438A1 (de) 2022-02-11 2023-08-17 Robert Bosch Gesellschaft mit beschränkter Haftung Pumpenrotor, sowie Pumpenlaufrad für einen Pumpenrotor

Family Cites Families (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE509458C (de) * 1929-02-23 1930-10-09 Naamlooze Vennootschap Konink Geschlossenes Schaufelrad fuer Kreiselpumpen, insbesondere fuer schaumbildende Fluessigkeiten
US1849557A (en) * 1929-06-12 1932-03-15 M T Davidson Company Centrifugal pump
US2344444A (en) * 1940-03-29 1944-03-14 Malczewski Jeremi Construction of turbomachines
GB537727A (en) * 1940-04-03 1941-07-03 Coventry Climax Eng Ltd Improvements in centrifugal pumps
DE737000C (de) * 1941-09-28 1943-07-03 Holstein & Kappert Maschf Kreiselpumpe fuer Milch, Rahm oder andere fluessige Nahrungsmittel
DE906975C (de) * 1950-05-03 1954-03-18 Licentia Gmbh Laufrad fuer radiale Turbokompressoren
GB728972A (en) * 1952-09-19 1955-04-27 English Electric Co Ltd Improvements in and relating to hydraulic turbines and pumps
US3025069A (en) * 1957-01-14 1962-03-13 Bell & Gossett Co Seat for rotary mechanical seals
FR2312671A1 (fr) * 1975-05-30 1976-12-24 Creusot Loire Procede de realisation de roue a aubes centrifuge et roue obtenue par ce procede
FI61233C (fi) * 1978-08-23 1982-06-10 Nokia Oy Ab Vinghjul hos en centrifugalflaekt saerskilt en hoegtrycksflaekt
GB2067673B (en) * 1980-01-22 1983-08-24 Mercantile Ab Oy Centrifugal blower impeller
DE3517499A1 (de) * 1985-05-15 1986-11-20 Klein, Schanzlin & Becker Ag, 6710 Frankenthal Laufrad
SU1373883A1 (ru) * 1986-01-17 1988-02-15 Производственное объединение "Невский завод" им.В.И.Ленина Рабочее колесо центробежного компрессора
DE3702016A1 (de) * 1987-01-24 1988-08-04 Klein Schanzlin & Becker Ag Einrichtung zur befestigung eines kreiselpumpenlaufrades aus einem sproeden werkstoff
US4720242A (en) * 1987-03-23 1988-01-19 Lowara, S.P.A. Centrifugal pump impeller

Also Published As

Publication number Publication date
ATE72883T1 (de) 1992-03-15
DE3731161A1 (de) 1989-05-03
CN1015068B (zh) 1991-12-11
DE3868643D1 (de) 1992-04-02
IN169694B (it) 1991-12-07
DE3731161C2 (de) 1996-12-12
WO1989002538A1 (fr) 1989-03-23
US5082425A (en) 1992-01-21
CA1321103C (en) 1993-08-10
EP0386010A1 (de) 1990-09-12
CN1032063A (zh) 1989-03-29

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