EP2232080B1 - Laufrad für eine pumpe - Google Patents

Laufrad für eine pumpe Download PDF

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Publication number
EP2232080B1
EP2232080B1 EP09703931A EP09703931A EP2232080B1 EP 2232080 B1 EP2232080 B1 EP 2232080B1 EP 09703931 A EP09703931 A EP 09703931A EP 09703931 A EP09703931 A EP 09703931A EP 2232080 B1 EP2232080 B1 EP 2232080B1
Authority
EP
European Patent Office
Prior art keywords
impeller
side cover
pressure
suction
cover disk
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.)
Not-in-force
Application number
EP09703931A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP2232080A1 (de
Inventor
Gerald Feichtinger
Martin Schober
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.)
Bitter Engineering & Systemtechnik GmbH
Original Assignee
Bitter Engineering & Systemtechnik GmbH
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 Bitter Engineering & Systemtechnik GmbH filed Critical Bitter Engineering & Systemtechnik GmbH
Publication of EP2232080A1 publication Critical patent/EP2232080A1/de
Application granted granted Critical
Publication of EP2232080B1 publication Critical patent/EP2232080B1/de
Not-in-force 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
    • F04D29/2205—Conventional flow pattern
    • F04D29/2222—Construction and assembly

Definitions

  • the invention relates to an impeller for a pump, in particular for a cooling water pump of an internal combustion engine, with an impeller body with a hub, a suction-side cover plate with a central opening for sucking a pumped medium and at least one blade, which is integrally connected to the suction-side cover plate and the an inner portion in the region of the central opening and an outer portion in the region of the suction-side cover disk, wherein the blade in the inner portion three-dimensionally curved and formed in the outer portion is substantially two-dimensional, wherein the impeller is produced in a casting process and each blade free of Overlaps and undercuts is.
  • the impellers of radial pumps are predominantly designed as so-called closed two-dimensional impellers. This means that blades are trapped between two shrouds, forming inside the impeller closed flow channels. Such closed impellers allow the achievement of good pump efficiencies.
  • the disadvantage is that the production of such wheels is expensive. Such a production can take place, for example, in a two-part form in that, on the one hand, a cover disk with blades formed thereon and, on the other hand, the other cover disk are produced separately and connected to the final running wheel.
  • a solution is for example in the US 2,710,580 A shown.
  • the DE 40 40 200 A shows such a solution in which the impeller has a pressure-side cover plate and a suction-side cover plate, between which the blades are arranged, wherein the suction-side cover plate has a central opening.
  • the vanes are arranged between the cover disks, wherein the suction-side cover disk has a central opening whose inner diameter is greater than the outer diameter of the pressure-side cover disk.
  • the DE 197 42 023 A discloses an impeller for a pump with spatially curved blades, which is composed of a plurality of radial segments for ease of manufacture. In addition, a cover disc is placed, so that a closed impeller is created.
  • the above statements apply mutatis mutandis.
  • an impeller for a pump which has a suction-side cover plate with a central opening for sucking a pumped medium and at least one blade integrally connected to the suction-side cover disk.
  • the blades are curved three-dimensionally and are curved two-dimensionally in the outer portion in the region of the suction-side cover disk.
  • 190 C1 is a composite of several parts impeller for turbomachines whose blades are fixed by means of a ring member or attached to the individual blades ring element parts directly in the frontal region of an impeller scar.
  • the impeller has a suction-side cover disk and a pressure-side cover disk.
  • the WO 89/02538 A1 describes a composite of several sheet metal parts centrifugal pump impeller. To achieve a rigid construction, the energy-transferring blades are attached only to a force-transmitting cover plate. The inlet region of the impeller forms a suction mouth, which is designed as a single part, the blade beginnings covered and secured thereto. A shovel-free cover disc covering the blade channels is secured to the blades between the impeller outlet and the maximum diameter of the suction mouth.
  • a multi-part centrifugal pump impeller which has blades with a pressure-side cover plate and a suction-side cover plate, wherein the suction-side cover plate is formed as a single part and connected to the impeller.
  • the US 2007/0147999 A describes an impeller for a pump with a full metal milled impeller main body with blades, which has a two-piece pressure-side cover consisting of an annular hub cover and a hub part. The cover is fixedly connected to the impeller main body. Overlapping and undercutting freedom is not required and not provided by the tensioning manufacturing process. Since the blades overlap in the suction mouth region, a 5-axis milling machine is required for the production, resulting in relatively high manufacturing costs for the impeller. A cost-effective mass production is therefore not possible.
  • the EP 1 533 104 A discloses a method for producing an impeller for a centrifugal pump, wherein a first part, which consists of a pressure-side cover plate with connection piece for the drive, on which blades are arranged on its side facing away from the connection piece, is manufactured as an individual part made of plastic in an injection molding process. Subsequently, a second part made of plastic, which is a suction-side cover plate and is provided on its inside with grooves which are complementary to the pressure-side cover plate facing away from edges of the blades, placed on the first part.
  • each of the pressure-side cover plate facing away from the edges of the blades engages in a complementarily shaped groove of the suction-side cover plate, whereby a connection of the first part takes place with the second part.
  • the two parts are joined together by gluing and / or ultrasonic or laser welding.
  • the disadvantage is that due to the overlap of the impeller blades a complex tool with folding and screw slide is required, the number of cavities is limited to 2. This causes a relatively high price per part. Due to the constraint that the blades into the grooves of the suction-side cover disk intervene, these must be complementary to the blades, but at the same time be made demouldable.
  • the publication US 4,720,242 A shows an impeller for a centrifugal pump, which is made in a sheet metal processing process.
  • the impeller main body is formed by a pressure-side cover disk and rotor blades, wherein the pressure-side cover disk and the impeller blades are not integral.
  • a portion of the two-dimensional curved blades is designed to be movable.
  • an impeller for a radial pump which is formed from a pourable or injectable polymer material and consists of two spaced-apart substantially radially directed discs, which are interconnected by two-dimensionally curved blades.
  • the pressure-side cover plate is designed in two parts, wherein a part is formed by the one hub part forming impeller main body and the second part by a locking ring. The connection of the two parts takes place cohesively or positively.
  • the object of the invention is to avoid these disadvantages and to achieve an improvement in the efficiency compared to known Laufradaus enclosureen with ease of manufacture of the impeller.
  • the impeller has a pressure-side cover plate which is formed as a separate part and rotatably connected to the impeller body and that the pressure-side cover plate on the side facing the blade at least one corresponding to the end face and the profile of the blade shaped groove-like depression for the blade for positive connection with this.
  • This allows the impeller with two- and three-dimensional efficiency optimized shaped blades are made in a simple manner, which are avoided by the pressure-side cover of the impeller flow losses to wake turbulence.
  • the impeller according to the invention thus combines the advantages of semi-open impellers with three-dimensionally curved blades with closed impellers.
  • the impeller Due to the semi-open design of the impeller, three-dimensionally curved blade structures can also be produced without problems even in mass production. Thereafter, the impeller is rotatably connected to the pressure-side cover plate, so that closed, spatially curved flow channels in the impeller arise.
  • the impeller can be made in a two-piece mold and by simple translational movements of the two mold halves be removed from the mold.
  • the impeller can be produced in a simple manner, for example in a die casting process or in a plastic injection molding process.
  • the diameter of the pressure-side cover plate corresponds to at least the diameter of an adjacent annular space which is formed between the impeller shaft and the housing. If the annular space is bounded laterally by a shaft seal, then it can be provided that the diameter of the pressure-side cover disk substantially corresponds to the diameter of a shaft seal defining the annular space.
  • a manufacturing moderately simple embodiment of the invention provides that the pressure-side cover plate is made plan.
  • the wall thickness of the pressure-side cover plate corresponds approximately to the wall thickness of the suction-side cover plate.
  • Output-side pressure losses can be kept as small as possible if the diameter of the pressure-side cover disk substantially corresponds to the diameter of the suction-side cover disk. It is particularly advantageous if the flow surface of the pressure-side cover plate is formed running with the side surface of the output-side pressure spiral.
  • the radial pumps shown in the figures each consist of a housing 1, shown only partially, with a bearing part 2 and a housing outer wall 23.
  • bearing 3 By only schematically illustrated bearing 3 is a pump shaft 4 mounted at one end an impeller 5 is attached.
  • a pump cover 7 is fixed, which surrounds the suction chamber 8 of the pump.
  • the pressure chamber 9 of the pump In the radial direction outside of the impeller 5, the pressure chamber 9 of the pump is arranged.
  • a running example of a mechanical seal shaft seal 10 seals the suction chamber 8 and pressure chamber 9 relative to the bearing part 2 from.
  • the impeller 5 has an impeller body 5a with a hub 11 which is rotatably connected to the impeller shaft 4. From the outer periphery of the hub 11 go from blades 13, which are designed to convey the fluid. The blades 13 are integrally connected to a suction-side cover plate 14, which has a central opening 15, is sucked through the conveying medium. On the opposite side of the semi-open running wheel body 5a is rotatably connected to a pressure-side cover plate 24.
  • the pressure-side cover plate 24 can be connected by means of a press fit with the impeller body 5a.
  • the wall thickness s 1 of the pressure-side cover plate 24 corresponds approximately to the wall thickness s 2 of the suction-side cover plate 14.
  • the size and shape of the pressure-side cover plate 24 is in the in the Fig. 1 to Fig. 11 variants shown differently.
  • the blades 13 have an inner portion 13a in the region of the opening 15 and an outer portion 13b in the region of the suction-side cover plate 14.
  • the diameter d of the opening 15 in the exemplary embodiment is about half the diameter D of the impeller. 5
  • the inner portion 13a of the blades 13 is helically curved, but free of overlaps or overlaps in the axial direction, to ensure easy releasability.
  • the blades 13 apart from any cast bevels, a rectangular cross-section which is perpendicular to the suction-side cover plate 14 to secure here also a simple demolding.
  • a convex surface 16 of the blades 13 extends smoothly from the inner portion 13a to the outer portion 13b. Opposite the convex surface 16, a concave surface 17 is formed. In the concave surface 17, an edge 18 is formed from the inner portion 13a to the outer portion 13b, which is required by casting.
  • the suction-side cover plate 14 is rounded in the transition to the opening 15 at 20 in order to achieve optimum flow deflection.
  • An axial projection 21 in the region of the opening 15 enables a possible flow optimization.
  • the blades 13 on the pressure side on an end face 22 which - at least partially - forms the support for the pressure-side cover plate 24.
  • the End face 22 may lie in a plane perpendicular to the axis 5 'of the impeller 5 ( Fig. 1 , such as Fig. 5 to Fig. 7 ) or convexly curved toward the pressure-side cover disk 24.
  • Fig. 1 shows an embodiment in which the diameter d 1 of the pressure-side cover plate 24 substantially corresponds to the diameter of the shaft seal 10, which is arranged in a spanned between the impeller shaft 4 and the housing 2 annular space 25.
  • the pressure-side cover plate 24 turbulence in the annular space 25 are avoided by the impeller 5.
  • Fig. 2 shows an embodiment in which the pressure-side cover plate 24 slightly convex and slightly concave to form flow channels on the blades 13 facing side 24a. This makes it possible to reduce the flow losses.
  • the Fig. 5 to Fig. 11 show embodiments in which the diameter d 1 of the pressure-side cover plate 24 is approximately equal to the diameter d 2 of the suction-side cover plate 14.
  • the pressure-side cover plate 24 has a substantially larger diameter than the annulus 25. This can flow losses due to turbulence and Ablations on the pressure side of the impeller 5 are further reduced.
  • the pressure-side cover plate 24 on the side facing the blades 13 side 24a corresponding to the end faces 22 of the blades 13 shaped recesses 26 on.
  • the end faces 22 of the blades 13 come to lie in the recesses 26 of the pressure-side cover plate 24, whereby a positive rotational connection of the impeller 5 and the pressure-side cover plate 24 is made, wherein impeller 5 and the pressure-side cover plate 24 may be interconnected by a press connection.
  • impeller 5 With the described impeller 5 according to the invention pumps can be produced at extremely high efficiency cost, the efficiency of pumps with closed wheels with two-dimensional blades surpasses.
  • the impeller 5 is very easy to produce by casting due to its ease of removal from the mold. Moreover, such an impeller 5 has excellent cavitation properties.
  • the impeller 5 according to the invention is particularly suitable for the conversion and upgrade of pumps with a relatively large annulus 25, without the pump housing 2 must be replaced or changed.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
EP09703931A 2008-01-25 2009-01-20 Laufrad für eine pumpe Not-in-force EP2232080B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
AT0011408A AT506342B1 (de) 2008-01-25 2008-01-25 Laufrad für eine pumpe
PCT/EP2009/050602 WO2009092711A1 (de) 2008-01-25 2009-01-20 Laufrad für eine pumpe

Publications (2)

Publication Number Publication Date
EP2232080A1 EP2232080A1 (de) 2010-09-29
EP2232080B1 true EP2232080B1 (de) 2012-03-14

Family

ID=40513933

Family Applications (1)

Application Number Title Priority Date Filing Date
EP09703931A Not-in-force EP2232080B1 (de) 2008-01-25 2009-01-20 Laufrad für eine pumpe

Country Status (5)

Country Link
US (1) US20100316497A1 (pt)
EP (1) EP2232080B1 (pt)
AT (2) AT506342B1 (pt)
BR (1) BRPI0906780B1 (pt)
WO (1) WO2009092711A1 (pt)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102011012074A1 (de) * 2011-02-23 2012-08-23 Wilo Se Laufrad einer Kreiselpumpe
US20140030099A1 (en) * 2012-07-27 2014-01-30 GM Global Technology Operations LLC Pump impeller
DE102014201487B3 (de) * 2014-01-28 2015-03-05 Bühler Motor GmbH Kreiselpumpenlaufrad
AT517163B1 (de) 2015-05-13 2019-08-15 Bitter Eng & Systemtechnik Gmbh Kreiselpumpe
US10584713B2 (en) 2018-01-05 2020-03-10 Spectrum Brands, Inc. Impeller assembly for use in an aquarium filter pump and methods
DE102020123517B4 (de) 2020-09-09 2024-06-06 Nidec Gpm Gmbh Laufrad für eine Zentrifugalflüssigkeitspumpe sowie Zentrifugalflüssigkeitspumpe aufweisend das Laufrad und Kraftfahrzeug aufweisend eine solche Zentrifugalfluidpumpe
CN116398351B (zh) * 2023-03-02 2025-07-04 大唐水电科学技术研究院有限公司 水轮机电液调节系统转速死区的测试方法

Family Cites Families (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2710580A (en) * 1946-10-29 1955-06-14 Kellogg M W Co Vaned rotor
US3107627A (en) 1958-06-27 1963-10-22 Stalker Corp Rotor for radial flow pumping means
JPS59165895A (ja) 1983-03-09 1984-09-19 Kubota Ltd 遠心うず巻ポンプの羽根車
DE3566294D1 (en) * 1984-05-24 1988-12-22 Moh 9 Proprietary Limited An impeller for a pump
DE3611910A1 (de) 1986-04-09 1987-10-15 Schaeffler Waelzlager Kg Laufrad fuer eine radialpumpe
US4720242A (en) 1987-03-23 1988-01-19 Lowara, S.P.A. Centrifugal pump impeller
DE3731161C2 (de) 1987-09-17 1996-12-12 Klein Schanzlin & Becker Ag Kreiselpumpenlaufrad
DE3839190C1 (pt) 1988-11-18 1990-04-19 Ksb Aktiengesellschaft, 6710 Frankenthal, De
DE4040200C2 (de) * 1990-12-15 1994-11-17 Freudenberg Carl Fa Kühlmittelpumpe zur Montage an dem Pumpengehäuse einer Brennkraftmaschine
DE19742023B4 (de) 1997-09-24 2006-07-13 Beez, Günther, Dipl.-Ing. Laufrad
DE10050108A1 (de) 2000-10-09 2002-06-06 Allweiler Ag Laufrad für eine Kreiselpumpe
AT413872B (de) * 2002-10-17 2006-06-15 Bitter Engineering & Systemtec Laufrad für eine pumpe
DE10354749A1 (de) 2003-11-21 2005-06-23 Siemens Ag Verfahren zur Herstellung eines Laufrades für eine Kreiselpumpe
DE102005031589A1 (de) * 2005-07-06 2007-01-11 Schaeffler Kg Wasserpumpenflügelrad
US7628586B2 (en) 2005-12-28 2009-12-08 Elliott Company Impeller
US7762778B2 (en) * 2007-05-17 2010-07-27 Kurz-Kasch, Inc. Fan impeller

Also Published As

Publication number Publication date
BRPI0906780B1 (pt) 2020-03-31
AT506342A1 (de) 2009-08-15
ATE549517T1 (de) 2012-03-15
WO2009092711A1 (de) 2009-07-30
US20100316497A1 (en) 2010-12-16
BRPI0906780A2 (pt) 2015-07-14
EP2232080A1 (de) 2010-09-29
AT506342B1 (de) 2011-03-15

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