EP0750119A1 - Pump impeller - Google Patents

Pump impeller Download PDF

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Publication number
EP0750119A1
EP0750119A1 EP95117565A EP95117565A EP0750119A1 EP 0750119 A1 EP0750119 A1 EP 0750119A1 EP 95117565 A EP95117565 A EP 95117565A EP 95117565 A EP95117565 A EP 95117565A EP 0750119 A1 EP0750119 A1 EP 0750119A1
Authority
EP
European Patent Office
Prior art keywords
impeller
blade
pump
blades
thickening
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
EP95117565A
Other languages
German (de)
French (fr)
Other versions
EP0750119B1 (en
Inventor
Manfred Zelder
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.)
Wilo GmbH
Original Assignee
Wilo GmbH
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Filing date
Publication date
Application filed by Wilo GmbH filed Critical Wilo GmbH
Publication of EP0750119A1 publication Critical patent/EP0750119A1/en
Application granted granted Critical
Publication of EP0750119B1 publication Critical patent/EP0750119B1/en
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
    • F04D29/2238—Special flow patterns
    • F04D29/225—Channel wheels, e.g. one blade or one flow channel
    • 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
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
    • F05C2225/00—Synthetic polymers, e.g. plastics; Rubber

Definitions

  • the invention relates to a pump impeller of a radial centrifugal pump, in particular a submersible motor pump with two curved blades, which are fixed to a disc close to the impeller hub, the two blades projecting freely into the pump chamber on the suction side without being fixed to another impeller disc (half-open impeller) .
  • the object of the invention is to improve the blockage of a radial centrifugal pump of the type mentioned in the introduction with a simple construction.
  • this object is achieved in that the initial area of the blade impinging on the liquid, in particular the leading edge of one of the two blades, has a greater thickness than the initial area of the second blade.
  • the impeller according to the invention does not buy the two-bladed design with an increased risk of clogging, but this quietly working impeller is similarly low in clogging as a single-bladed one.
  • the thickening of the initial region of the first blade is arranged on the side of the blade facing away from the impeller axis.
  • the thickening should also pass into the front curve of the front edge of the blade.
  • a reduction in the unbalance is achieved in that the unbalance generated by the thickening is eliminated by a reduction in mass on the same impeller side or by an increase in mass on the opposite impeller side. It is also an advantage if the impeller is made of plastic.
  • the impeller 1 of a radial centrifugal pump which can be used as a submersible pump, has a circular disk 2, on the rear of which a hub 3 is coaxially formed, in which a bushing 4 can be cast in order to fasten the impeller to the shaft of an electric motor.
  • the blades 5 and 6 are formed in a rotationally symmetrical manner opposite one another on the plastic disk 2 and taper in their thickness D towards the pump inlet side.
  • the impeller shown in Figure 1 rotates in the direction of arrow 7 so that the blade leading edges 5a and 6a first meet the liquid to be conveyed.
  • These blade leading edges together with an adjoining area are referred to as blade start areas 5b, 6b. While outside the blade start areas 5b, 6b the two blades 5, 6 are identical, there is a difference in these blade start areas:
  • the thickness D1 of the blade beginning area 5b is greater than the thickness D2 of the blade starting area 6b, the second blade 6.
  • the additional thickening of the starting area 5b of the first blade 5 is open molded on the side of the blade facing away from the impeller axis 8.
  • the thickness D 1 is only slightly larger than the thickness D2 (0.1-4mm or 5-40% larger than D2), the effect is considerable for greater freedom from clogging.
  • the length of the thickened blade start area 5b is 1/20 to 1/4 of the total length of the first blade 5.
  • the thickening merges with the curve at the front edge 5a of the blade, so that the first blade 5 has the same aerodynamic shape as the second blade 6.
  • the impeller In order to compensate for the imbalance caused by the thickening, the impeller has a reduction in mass on the side of FIG. 5 or an increase in mass on the opposite side.

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  • 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

The rotor is fitted to a centrifugal pump, especially a submerged pump, and has two curved blades (5,6) which are fixed to one rotor disc near the hub. Both blades project freely into the pump volume on the suction side, and are not attached to another rotor disc. One (5) of the blades has a greater thickness in the region (5b) which the incident fluid first encounters, especially the blade leading edge (5a), than the corresponding dimension on the second blade. The thickening (V) may be arranged on the side of the blade which faces away from the rotor axis, and may merge into the frontal curvature of the blade leading edge.

Description

Die Erfindung betrifft ein Pumpenlaufrad einer Radialkreiselpumpe insbesondere einer Tauchmotorpumpe mit zwei gekrümmten Schaufeln, die an einer der Laufradnabe nahen Scheibe fest sind, wobei an der Saugseite die beiden Schaufeln frei in den Pumpenraum ragen, ohne an einer weiteren Laufradscheibe fest zu sein (halboffenes Laufrad).The invention relates to a pump impeller of a radial centrifugal pump, in particular a submersible motor pump with two curved blades, which are fixed to a disc close to the impeller hub, the two blades projecting freely into the pump chamber on the suction side without being fixed to another impeller disc (half-open impeller) .

Für verstopfungsfreie Pumpen ist es bekannt, das Laufrad mit einer einzigen Schaufel auszuführen. Solche einschaufeligen Laufräder haben einen geringeren Wirkungsgrad und führen zu einer sogenannten hydrodynamischen Unwucht, die durch das asymmetrische Vorbeilaufen der einzigen Schaufel am Druckstutzen entsteht. Hierbei addiert noch die mechanische Unwucht zur hydrodynamischen Unwucht, wobei es bekannt ist, der mechanischen Unwucht durch eine unsymmetrische Verteilung der Massen im Laufrad entgegenzuwirken.For blockage-free pumps, it is known to design the impeller with a single blade. Such single-bladed impellers are less efficient and lead to a so-called hydrodynamic imbalance, which is caused by the asymmetrical running of the single blade past the pressure nozzle. Here, the mechanical unbalance is added to the hydrodynamic unbalance, and it is known to counteract the mechanical unbalance by asymmetrically distributing the masses in the impeller.

Diese Unwuchtprobleme sind bei zweischaufeligen Laufrädern nicht gegeben. Diese Laufräder führen aber leichter zu einem Verstopfen der Pumpe insbesondere bei Abwässern mit Stoffresten wie z.B. einem Lappen. Ein Lappen kann sich über beide Schaufeln legen und damit an beiden Schaufeln hängenbleiben.These unbalance problems do not exist with two-bladed impellers. However, these impellers are more likely to clog the pump, especially in the case of waste water with material residues such as a rag. A rag can overlap both blades and get stuck on both blades.

Aufgabe der Erfindung ist es, bei einfacher Konstruktion die Verstopfungsfreiheit einer Radialkreiselpumpe der eingangs genannten Art zu verbessern.The object of the invention is to improve the blockage of a radial centrifugal pump of the type mentioned in the introduction with a simple construction.

Diese Aufgabe wird erfindungsgemäß dadurch gelöst, daß der auf die Flüssigkeit zuerst auftreffende Schaufelanfangsbereich insbesondere die Schaufelvorderkante einer der beiden Schaufeln eine größere Dicke aufweist als der Anfangsbereich der zweiten Schaufel.According to the invention, this object is achieved in that the initial area of the blade impinging on the liquid, in particular the leading edge of one of the two blades, has a greater thickness than the initial area of the second blade.

Gelangt in ein solches Laufrad ein üblicherweise zur Verstopfung führendes Teil wie z.b. ein Stoffrest, ein Lappen oder eine Strumpfhose, so bleibt dieser in der Regel nicht mittig hängen, sondern die im Anfangsbereich ungleich dicken Schaufeln sorgen dafür, daß das Laufrad sich von diesem Teil schnell lösen kann und es damit weitergefördert wird. Während beim Laufrad mit zwei gleichen Schaufeln der verstopfende Lappen "nicht weiß", für welche Schaufel er sich entscheiden soll, und damit mittig hängen bleibt, wird bei dem Laufrad mit ungleichartigen Schaufeln dafür gesorgt, daß aufgrund dieser Ungleichartigkeit das zur Verstopfung führende Teil sicher weitertransportiert wird.If such an impeller gets a part that usually leads to constipation, e.g. a remnant of cloth, a rag or tights, this usually does not get caught in the middle, but the blades of uneven thickness in the beginning ensure that the impeller can quickly detach from this part and it is conveyed further. While with the impeller with two identical blades, the clogging rag "does not know" which blade to choose, and thus gets stuck in the middle, the impeller with dissimilar blades ensures that the part leading to the blockage is transported safely due to this unevenness becomes.

Somit erkauft sich das erfindungsgemäße Laufrad die Zweischaufeligkeit nicht mit einer erhöhten Verstopfungsgefahr, sondern dieses ruhig arbeitende Laufrad ist ähnlich verstopfungsarm wie ein einschaufeliges.Thus, the impeller according to the invention does not buy the two-bladed design with an increased risk of clogging, but this quietly working impeller is similarly low in clogging as a single-bladed one.

Besonders vorteilhaft ist hierbei, wenn die Verdickung des Anfangsbereiches der ersten Schaufel auf der der Laufradachse abgewandten Seite der Schaufel angeordnet ist. Auch sollte die Verdickung in die vordere Rundung der Schaufelvorderkante übergehen.It is particularly advantageous here if the thickening of the initial region of the first blade is arranged on the side of the blade facing away from the impeller axis. The thickening should also pass into the front curve of the front edge of the blade.

Eine Verringerung der Unwucht wird dadurch erreicht, daß die durch die Verdickung erzeugte Unwucht durch eine Massenverringerung auf derselben Laufradseite oder durch eine Massenerhöhung auf der gegenüberliegenden Laufradseite aufgehoben ist. Auch ist von Vorteil, wenn das Laufrad aus Kunststoff ist.A reduction in the unbalance is achieved in that the unbalance generated by the thickening is eliminated by a reduction in mass on the same impeller side or by an increase in mass on the opposite impeller side. It is also an advantage if the impeller is made of plastic.

Ein Ausführungsbeispiel der Erfindung ist in der Zeichnung dargestellt und wird im folgenden näher beschrieben. Es zeigen:

Figur 1:
Eine Draufsicht auf das Laufrad in Ansaugrichtung und
Figur 2:
einen Schnitt durch das Laufrad nach A-D in Figur 1.
An embodiment of the invention is shown in the drawing and will be described in more detail below. Show it:
Figure 1:
A top view of the impeller in the suction direction
Figure 2:
a section through the impeller according to AD in Figure 1.

Das Laufrad 1 einer Radialkreiselpumpe, die als Tauchmotorpumpe einsetzbar ist, weist eine kreisförmige Scheibe 2 auf, an deren Rückseite koaxial eine Nabe 3 angeformt ist, in der eine Buchse 4 eingegossen sein kann, um das Laufrad an der Welle eines Elektromotors zu befestigen.The impeller 1 of a radial centrifugal pump, which can be used as a submersible pump, has a circular disk 2, on the rear of which a hub 3 is coaxially formed, in which a bushing 4 can be cast in order to fasten the impeller to the shaft of an electric motor.

Auf der Vorderseite der Scheibe 2 stehen zwei Schaufeln 5, 6 vor, die frei in den Pumpenraum ragen, so daß es sich um ein halboffenes Laufrad handelt. Die Schaufeln 5 und 6 sind drehsymmetrisch einander gegenüberliegend an der Kunststoffscheibe 2 angeformt und verjüngen sich in ihrer Dicke D zur Pumpeneinlaßseite hin.On the front of the disc 2 are two blades 5, 6, which protrude freely into the pump chamber, so that it is a half-open impeller. The blades 5 and 6 are formed in a rotationally symmetrical manner opposite one another on the plastic disk 2 and taper in their thickness D towards the pump inlet side.

Das in Figur 1 dargestellte Laufrad dreht sich in Richtung des Pfeiles 7, so daß die Schaufelvorderkanten 5a und 6a zuerst auf die zu fördernde Flüssigkeit treffen. Diese Schaufelvorderkanten werden zusammen mit einem daran anschließenden Bereich als Schaufelanfangsbereiche 5b, 6b bezeichnet. Während außerhalb der Schaufelanfangsbereiche 5b, 6b die beiden Schaufeln 5, 6 gleich ausgeführt sind, besteht ein Unterschied in diesen Schaufelanfangsbereichen:The impeller shown in Figure 1 rotates in the direction of arrow 7 so that the blade leading edges 5a and 6a first meet the liquid to be conveyed. These blade leading edges together with an adjoining area are referred to as blade start areas 5b, 6b. While outside the blade start areas 5b, 6b the two blades 5, 6 are identical, there is a difference in these blade start areas:

Bei einer der beiden Schaufeln, in diesem Fall bei der ersten Schaufel 5, ist die Dicke D1 des Schaufelanfangsbereiches 5b größer als die Dicke D2 des Schaufelanfangsbereiches 6b, der zweiten Schaufel 6. Im Ausführungsbeispiel ist die zusätzliche Verdickung des Anfangsbereiches 5b der ersten Schaufel 5 auf der der Laufradachse 8 abgewandten Seite der Schaufel angeformt. Obwohl die Dicke D 1 nur wenig größer ist als die Dicke D2 (0,1-4mm bzw. 5-40% größer als D2), so ist die Wirkung für eine größere Verstopfungsfreiheit erheblich.In one of the two blades, in this case in the first blade 5, the thickness D1 of the blade beginning area 5b is greater than the thickness D2 of the blade starting area 6b, the second blade 6. In the exemplary embodiment, the additional thickening of the starting area 5b of the first blade 5 is open molded on the side of the blade facing away from the impeller axis 8. Although the thickness D 1 is only slightly larger than the thickness D2 (0.1-4mm or 5-40% larger than D2), the effect is considerable for greater freedom from clogging.

Die Länge des verdickten Schaufelanfangsbereiches 5b beträgt 1/20 bis 1/4 der Gesamtlänge der ersten Schaufel 5. Die Verdickung geht an der Schaufelvorderkante 5a in deren Rundung über, so daß die erste Schaufel 5 gleich strömungsgünstig geformt ist, wie die zweite Schaufel 6.The length of the thickened blade start area 5b is 1/20 to 1/4 of the total length of the first blade 5. The thickening merges with the curve at the front edge 5a of the blade, so that the first blade 5 has the same aerodynamic shape as the second blade 6.

Um die durch die Verdickung erzeugte Unwucht auszugleichen, besitzt das Laufrad auf der Seite der 5 eine Massenverringerung oder auf der gegenüberliegenden Seite eine Massenerhöhung.In order to compensate for the imbalance caused by the thickening, the impeller has a reduction in mass on the side of FIG. 5 or an increase in mass on the opposite side.

Claims (5)

Pumpenlaufrad (1) einer Radialkreiselpumpe insbesondere einer Tauchmotorpumpe mit zwei gekrümmten Schaufeln (5, 6), die an einer der Laufradnabe (3) nahen Scheibe fest sind, wobei an der Saugseite die beiden Schaufeln frei in den Pumpenraum ragen, ohne an einer weiteren Laufradscheibe fest zu sein (halboffenes Laufrad), dadurch gekennzeichnet, daß der auf die Flüssigkeit zuerst auftreffende Schaufelanfangsbereich (5b) insbesondere die Schaufelvorderkante (5a) einer der beiden Schaufeln (5) eine größere Dicke (D1) aufweist als der Anfangsbereich der zweiten Schaufel (6).Pump impeller (1) of a radial centrifugal pump, in particular a submersible motor pump with two curved blades (5, 6), which are fixed to a disc close to the impeller hub (3), the two blades protruding freely into the pump chamber on the suction side, without another impeller disc to be firm (semi-open impeller), characterized in that the blade start area (5b) which strikes the liquid first, in particular the blade front edge (5a) of one of the two blades (5), has a greater thickness (D1) than the start area of the second blade (6 ). Pumpenlaufrad nach Anspruch 1, dadurch gekennzeichnet, daß die Verdickung (V) des Anfangsbereiches (5b) der ersten Schaufel (5) auf der der Laufradachse (8) abgewandten Seite der Schaufel angeordnet ist.Pump impeller according to claim 1, characterized in that the thickening (V) of the initial region (5b) of the first blade (5) is arranged on that side of the blade which is remote from the impeller axis (8). Pumpenlaufrad nach Anspruch 1, dadurch gekennzeichnet, daß die Verdickung (V) in die vordere Rundung der Schaufelvorderkante (5a) übergeht.Pump impeller according to claim 1, characterized in that the thickening (V) merges into the front curve of the blade front edge (5a). Pumpenlaufrad nach einem der vorherigen Ansprüche, dadurch gekennzeichnet, daß die durch die Verdickung (V) erzeugte Unwucht durch eine Massenverringerung auf derselben Laufradseite oder durch eine Massenerhöhung auf der gegenüberliegenden Laufradseite aufgehoben ist.Pump impeller according to one of the preceding claims, characterized in that the unbalance produced by the thickening (V) is eliminated by a reduction in mass on the same impeller side or by an increase in mass on the opposite impeller side. Pumpenlaufrad nach einem der vorherigen Ansprüche, dadurch gekennzeichnet, daß das Laufrad (1) aus Kunststoff ist.Pump impeller according to one of the preceding claims, characterized in that the impeller (1) is made of plastic.
EP95117565A 1995-06-19 1995-11-08 Pump impeller Expired - Lifetime EP0750119B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19521768A DE19521768A1 (en) 1995-06-19 1995-06-19 Pump impeller
DE19521768 1995-06-19

Publications (2)

Publication Number Publication Date
EP0750119A1 true EP0750119A1 (en) 1996-12-27
EP0750119B1 EP0750119B1 (en) 2000-05-10

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ID=7764431

Family Applications (1)

Application Number Title Priority Date Filing Date
EP95117565A Expired - Lifetime EP0750119B1 (en) 1995-06-19 1995-11-08 Pump impeller

Country Status (3)

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US (1) US5692880A (en)
EP (1) EP0750119B1 (en)
DE (2) DE19521768A1 (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2014029790A1 (en) * 2012-08-23 2014-02-27 Sulzer Pumpen Ag Pump for conveying effluent, impeller and base plate for such a pump

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Publication number Priority date Publication date Assignee Title
ES2195733B1 (en) * 2001-07-20 2005-08-16 Fagor, S.Coop. HYDRAULIC PUMP WITH FLOW GUIDE.
US6979174B2 (en) * 2003-10-01 2005-12-27 Schlumberger Technology Corporation Stage pump having composite components
JP4554189B2 (en) * 2003-11-26 2010-09-29 株式会社エンプラス Centrifugal impeller
US7544042B2 (en) * 2006-01-03 2009-06-09 Emerson Electric Co. Insert with sleeve for a molded impeller
DE102011007907B3 (en) * 2011-04-21 2012-06-21 Ksb Aktiengesellschaft Impeller for centrifugal pumps
CN103216452B (en) * 2013-04-25 2016-05-11 常州雷利电机科技有限公司 Draining pump
JP6488167B2 (en) * 2015-03-27 2019-03-20 株式会社荏原製作所 Centrifugal pump
AU201614369S (en) * 2016-08-12 2016-10-27 Weir Minerals Australia Ltd Impeller
USD810789S1 (en) * 2016-08-25 2018-02-20 Weir Minerals Australia Ltd. Pump impeller
USD810788S1 (en) * 2016-08-25 2018-02-20 Weir Minerals Australia Ltd. Pump impeller
DE102017221930A1 (en) * 2017-12-05 2019-06-06 KSB SE & Co. KGaA Impeller for wastewater pump

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US1864834A (en) * 1927-12-28 1932-06-28 Buffalo Steam Pump Company Centrifugal pump impeller
US1959710A (en) * 1931-09-21 1934-05-22 Chicago Pump Co Pump
US4063849A (en) * 1975-02-12 1977-12-20 Modianos Doan D Non-clogging, centrifugal, coaxial discharge pump
GB2053368A (en) * 1979-06-22 1981-02-04 Klein Schanzlin & Becker Ag An open impeller for a centrifugal pump
JPS61252893A (en) * 1985-05-02 1986-11-10 Hitachi Ltd Sewage and waste pump
EP0640768A1 (en) * 1993-08-24 1995-03-01 KSB Aktiengesellschaft Single-channel impeller for centrifugal pumps

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US553956A (en) * 1896-02-04 Explosive valve for blast-furnaces
US1754992A (en) * 1926-12-06 1930-04-15 American Well Works Centrifugal pump
US2265758A (en) * 1940-05-29 1941-12-09 Buffalo Pumps Inc Pump
US4087994A (en) * 1976-09-07 1978-05-09 The Maytag Company Centrifugal pump with means for precluding airlock
US4293280A (en) * 1980-08-27 1981-10-06 The United States Of America As Represented By The Secretary Of The Navy Transcavitating propeller
US4681508A (en) * 1984-11-14 1987-07-21 Kim Choong W Supercavitation centrifugal pump

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Publication number Priority date Publication date Assignee Title
US1864834A (en) * 1927-12-28 1932-06-28 Buffalo Steam Pump Company Centrifugal pump impeller
US1959710A (en) * 1931-09-21 1934-05-22 Chicago Pump Co Pump
US4063849A (en) * 1975-02-12 1977-12-20 Modianos Doan D Non-clogging, centrifugal, coaxial discharge pump
GB2053368A (en) * 1979-06-22 1981-02-04 Klein Schanzlin & Becker Ag An open impeller for a centrifugal pump
JPS61252893A (en) * 1985-05-02 1986-11-10 Hitachi Ltd Sewage and waste pump
EP0640768A1 (en) * 1993-08-24 1995-03-01 KSB Aktiengesellschaft Single-channel impeller for centrifugal pumps

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Title
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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2014029790A1 (en) * 2012-08-23 2014-02-27 Sulzer Pumpen Ag Pump for conveying effluent, impeller and base plate for such a pump
US10495092B2 (en) 2012-08-23 2019-12-03 Sulzer Management Ag Pump for conveying waste water as well as impeller and base plate for such a pump

Also Published As

Publication number Publication date
US5692880A (en) 1997-12-02
DE19521768A1 (en) 1997-01-02
DE59508322D1 (en) 2000-06-15
EP0750119B1 (en) 2000-05-10

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