EP2232080B1 - Impeller for a pump - Google Patents
Impeller for a pump Download PDFInfo
- 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
Links
- 239000000498 cooling water Substances 0.000 claims abstract description 4
- 238000002485 combustion reaction Methods 0.000 claims abstract description 3
- 238000005266 casting Methods 0.000 claims description 6
- 238000000034 method Methods 0.000 claims description 3
- 238000010276 construction Methods 0.000 abstract description 2
- 239000012526 feed medium Substances 0.000 abstract 1
- 238000004519 manufacturing process Methods 0.000 description 17
- 239000002184 metal Substances 0.000 description 4
- 229910052751 metal Inorganic materials 0.000 description 4
- 239000000243 solution Substances 0.000 description 3
- 230000000295 complement effect Effects 0.000 description 2
- 239000002131 composite material Substances 0.000 description 2
- 238000001746 injection moulding Methods 0.000 description 2
- 229910001208 Crucible steel Inorganic materials 0.000 description 1
- 229910001060 Gray iron Inorganic materials 0.000 description 1
- 238000002679 ablation Methods 0.000 description 1
- 238000004026 adhesive bonding Methods 0.000 description 1
- 238000006243 chemical reaction Methods 0.000 description 1
- 238000004512 die casting Methods 0.000 description 1
- 230000002349 favourable effect Effects 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 238000010327 methods by industry Methods 0.000 description 1
- 238000003801 milling Methods 0.000 description 1
- 238000005457 optimization Methods 0.000 description 1
- 239000002861 polymer material Substances 0.000 description 1
- 231100000241 scar Toxicity 0.000 description 1
- 238000000926 separation method Methods 0.000 description 1
- 238000005476 soldering Methods 0.000 description 1
- 230000007704 transition Effects 0.000 description 1
- 238000003466 welding Methods 0.000 description 1
Images
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.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
Description
Die Erfindung betrifft ein Laufrad für eine Pumpe, insbesondere für eine Kühlwasserpumpe einer Brennkraftmaschine, mit einem Laufradkörper mit einer Nabe, einer saugseitigen Deckscheibe mit einer zentralen Öffnung zum Ansaugen eines Fördermediums und mit mindestens einer Schaufel, die mit der saugseitigen Deckscheibe einstückig verbunden ist und die einen inneren Abschnitt im Bereich der zentralen Öffnung und einen äußeren Abschnitt im Bereich der saugseitigen Deckscheibe aufweist, wobei die Schaufel im inneren Abschnitt dreidimensional gekrümmt und im äußeren Abschnitt im Wesentlichen zweidimensional ausgebildet ist, wobei das Laufrad in einem Gussverfahren hergestellt ist und jede Schaufel frei von Überdeckungen und Hinterschneidungen ist.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.
Die Laufräder von Radialpumpen, wie sie etwa als Kühlwasserpumpen von Kraftfahrzeugen eingesetzt werden, sind überwiegend als sogenannte geschlossene zweidimensionale Laufräder ausgebildet. Dies bedeutet, dass Schaufeln zwischen zwei Deckscheiben eingeschlossen sind, wodurch sich innerhalb des Laufrades geschlossene Strömungskanäle ausbilden. Solche geschlossenen Laufräder ermöglichen die Erzielung von guten Pumpenwirkungsgraden. Nachteilig ist jedoch, dass die Herstellung solcher Laufräder aufwändig ist. Eine solche Herstellung kann beispielsweise in zweiteiliger Form dadurch erfolgen, dass einerseits eine Deckscheibe mit daran angeformten Schaufeln und andererseits die andere Deckscheibe getrennt voneinander hergestellt werden und zum endgültigen Laufrad verbunden werden. Eine solche Lösung ist beispielsweise in der
Um die Herstellung eines solchen Laufrades einfach und kostengünstig gestalten zu können, ist es wünschenswert ein Laufrad zu entwerfen, das mit einer einfachen zweiteiligen Gießform hergestellt werden kann. Die
Des weiteren ist es bekannt, durch den Einsatz von dreidimensional gekrümmten Schaufeln den Pumpenwirkungsgrad von Radialpumpen oder Axialpumpen verbessern zu können. Eine solche Lösung ist beispielsweise in der
Die
In der
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Die
Die
Die Veröffentlichung
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Weiters wird auch durch die
Aufgabe der Erfindung ist es, diese Nachteile zu vermeiden und bei einfacher Herstellbarkeit des Laufrades eine Verbesserung des Wirkungsgrades im Vergleich zu bekannten Laufradausführungen zu erzielen.The object of the invention is to avoid these disadvantages and to achieve an improvement in the efficiency compared to known Laufradausführungen with ease of manufacture of the impeller.
Erfindungsgemäß wird dies dadurch erreicht, dass das Laufrad eine druckseitige Deckscheibe aufweist, welche als separater Teil ausgebildet und fest mit dem Laufradkörper drehverbunden ist und dass die druckseitige Deckscheibe auf der der Schaufel zugewandten Seite zumindest eine entsprechend der Stirnfläche und dem Profil der Schaufel geformte nutartige Vertiefung für die Schaufel zur formschlüssigen Verbindung mit dieser aufweist. Dadurch kann das Laufrad mit zwei- und dreidimensional wirkungsgradoptimal geformten Laufschaufeln auf einfache Weise hergestellt werden, wobei durch die druckseitige Abdeckung des Laufrades Strömungsverluste zu Folge Verwirbelungen vermieden werden. Das erfindungsgemäße Laufrad vereinigt somit die Vorteile von halboffenen Laufrädern mit dreidimensional gekrümmten Schaufeln mit geschlossenen Laufrädern. Durch die halboffene Bauweise des Laufrades lassen sich dreidimensional gekrümmte Laufschaufelstrukturen auch in der Massenfertigung problemlos herstellen. Danach wird das Laufrad mit der druckseitigen Deckscheibe drehfest verbunden, so dass geschlossene, räumlich gekrümmte Strömungskanäle im Laufrad entstehen.According to the invention this is achieved in that 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. 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.
Durch die Vertiefungen wird mit einfachen Mitteln eine drehsichere Verbindung zwischen den beiden Teilen des Laufrades ermöglicht.Through the wells a rotationally secure connection between the two parts of the impeller is made possible by simple means.
Wenn die Schaufeln im inneren Abschnitt frei von Überdeckungen und Hinterschneidungen sind, das heißt, wenn die Hinterkante einer Schaufel in axialer Betrachtung vor der Vorderkante der nächsten Schaufel liegt, dann kann das Laufrad in einer zweiteiligen Form hergestellt werden und durch einfache translatorische Bewegungen der beiden Formhälften entformt werden.If the blades in the inner portion are free of overlaps and undercuts, that is, if the trailing edge of one blade is axially in front of the leading edge of the next blade, then 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.
Auf diese Weise kann das Laufrad in einfacher Weise, beispielsweise in einem Druckgussverfahren oder auch in einem Kunststoffspritzgussverfahren hergestellt werden. Es ist jedoch auch möglich, Stahlguss oder Graugussverfahren einzusetzen.In this way, the impeller can be produced in a simple manner, for example in a die casting process or in a plastic injection molding process. However, it is also possible to use cast steel or gray cast iron.
Bei Pumpen, bei denen zwischen Laufradwelle und Pumpengehäuse auf der Druckseite des Laufrades ein ringförmiger Totraum ausgebildet ist, ist es vorteilhaft, wenn der Durchmesser der druckseitigen Deckscheibe mindestens den Durchmesser eines angrenzenden Ringraumes entspricht, welcher zwischen Laufradwelle und Gehäuse gebildet ist. Wird der Ringraum durch eine Wellendichtung seitlich begrenzt, so kann vorgesehen sein, dass der Durchmesser der druckseitigen Deckscheibe im Wesentlichen dem Durchmesser einer den Ringraum begrenzenden Wellendichtung entspricht.In pumps in which between the impeller shaft and pump housing on the pressure side of the impeller, an annular dead space is formed, it is advantageous if 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.
Eine herstellungsmäßig besonders einfache Ausführung der Erfindung sieht vor, dass die druckseitige Deckscheibe plan ausgeführt ist.A manufacturing moderately simple embodiment of the invention provides that the pressure-side cover plate is made plan.
Ein besonders hoher Wirkungsgrad lässt sich dagegen erzielen, wenn die druckseitige Deckscheibe auf der den Laufschaufeln zugewandten Seite konkav gekrümmt ausgeführt ist. Um Gewicht und Herstellungskosten des Laufrades möglichst gering zu halten, entspricht die Wandstärke der druckseitigen Deckscheibe etwa der Wandstärke der saugseitigen Deckscheibe.On the other hand, a particularly high degree of efficiency can be achieved if the pressure-side cover disk is concavely curved on the side facing the rotor blades. In order to keep weight and manufacturing costs of the impeller as low as possible, the wall thickness of the pressure-side cover plate corresponds approximately to the wall thickness of the suction-side cover plate.
Ausgangsseitige Druckverluste können möglichst klein gehalten werden, wenn der Durchmesser der druckseitigen Deckscheibe im Wesentlichen dem Durchmesser der saugseitigen Deckscheibe entspricht. Dabei ist es besonders vorteilhaft, wenn die Strömungsfläche der druckseitigen Deckscheibe verlaufend mit der Seitenfläche der ausgangsseitigen Druckspirale ausgebildet ist.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.
Besonders günstig zur Erhöhung des Wirkungsgrades ist, wenn an der Deckscheibe im Bereich der Öffnung ein axialer Vorsprung vorgesehen ist, der in Richtung der Saugseite vorragt. Auf diese Weise ist es möglich, den strömungstechnisch besonders kritischen Einlaufbereich optimal auszubilden.Is particularly favorable for increasing the efficiency, if an axial projection is provided on the cover plate in the region of the opening, which projects in the direction of the suction side. In this way it is possible to optimally form the fluidically particularly critical inlet region.
Im Folgenden wird die Erfindung anhand von Figuren näher erläutert. Es zeigen:
- Fig. 1
- eine Pumpe mit einem erfindungsgemäßen Laufrad in einem Längsschnitt in einer ersten Ausführungsvariante;
- Fig. 2
- eine Pumpe mit einem erfindungsgemäßen Laufrad in einem Längsschnitt in einer zweiten Ausführungsvariante;
- Fig. 3
- das Laufrad aus
Fig. 2 in einer saugseitigen Schrägansicht; - Fig. 4
- das Laufrad in einer druckseitigen Schrägansicht;
- Fig. 5
- eine Pumpe mit einem erfindungsgemäßen Laufrad in einem Längsschnitt in einer dritten Ausführungsvariante;
- Fig. 6
- das Laufrad in einer saugseitigen Schrägansicht;
- Fig. 7
- das Laufrad in einer druckseitigen Schrägansicht;
- Fig. 8
- eine Pumpe mit einem erfindungsgemäßen Laufrad in einem Längsschnitt in einer vierten Ausführungsvariante;
- Fig. 9
- das Laufrad aus
Fig. 8 in einer saugseitigen Schrägansicht; - Fig. 10
- eine Pumpe mit einem erfindungsgemäßen Laufrad in einem Längsschnitt in einer fünften Ausführungsvariante;
- Fig. 11
- das Laufrad aus
Fig. 10 in einer druckseitigen Schrägansicht; und - Fig. 12
- das Laufrad in einer Explosionsdarstellung.
- Fig. 1
- a pump with an impeller according to the invention in a longitudinal section in a first embodiment;
- Fig. 2
- a pump with an impeller according to the invention in a longitudinal section in a second embodiment;
- Fig. 3
- the impeller off
Fig. 2 in a suction-side oblique view; - Fig. 4
- the impeller in a pressure-side oblique view;
- Fig. 5
- a pump with an impeller according to the invention in a longitudinal section in a third embodiment;
- Fig. 6
- the impeller in a suction-side oblique view;
- Fig. 7
- the impeller in a pressure-side oblique view;
- Fig. 8
- a pump with an impeller according to the invention in a longitudinal section in a fourth embodiment;
- Fig. 9
- the impeller off
Fig. 8 in a suction-side oblique view; - Fig. 10
- a pump with an impeller according to the invention in a longitudinal section in a fifth embodiment;
- Fig. 11
- the impeller off
Fig. 10 in a pressure-side oblique view; and - Fig. 12
- the impeller in an exploded view.
Die in den Figuren dargestellten Radialpumpen bestehen jeweils aus einem nur teilweise dargestellten Gehäuse 1, mit einem Lagerteil 2 und einer Gehäuseaußenwand 23. Durch ein nur schematisch dargestelltes Lager 3 ist eine Pumpenwelle 4 gelagert, an deren einem Ende ein Laufrad 5 befestigt ist. An der Gehäusewand 23 ist ein Pumpendeckel 7 befestigt, der den Saugraum 8 der Pumpe umschließt. In Radialrichtung außerhalb des Laufrades 5 ist der Druckraum 9 der Pumpe angeordnet. Eine beispielsweise als Gleitringdichtung ausgeführte Wellendichtung 10 dichtet Saugraum 8 und Druckraum 9 gegenüber dem Lagerteil 2 ab.The radial pumps shown in the figures each consist of a housing 1, shown only partially, with a
Das Laufrad 5 weist einen Laufradkörper 5a mit einer Nabe 11 auf, die mit der Laufradwelle 4 drehfest verbunden ist. Vom äußeren Umfang der Nabe 11 gehen Schaufeln 13 aus, die zur Förderung des Fördermediums ausgebildet sind. Die Schaufeln 13 sind einstückig mit einer saugseitigen Deckscheibe 14 verbunden, die eine zentralen Öffnung 15 aufweist, durch die Fördermedium angesaugt wird. Auf der gegenüberliegenden Seite ist der an sich halboffen ausgeführte Laufradkörper 5a mit einer druckseitigen Deckscheibe 24 drehfest verbunden. Die druckseitige Deckscheibe 24 kann dabei mittels eines Presssitzes mit dem Laufradkörper 5a verbunden sein. Die Wandstärke s1 der druckseitigen Deckscheibe 24 entspricht dabei etwa der Wandstärke s2 der saugseitigen Deckscheibe 14. Die Größe und die Form der druckseitigen Deckscheibe 24 ist in den in den
Die Schaufeln 13 besitzen einen inneren Abschnitt 13a im Bereich der Öffnung 15 und einen äußeren Abschnitt 13b im Bereich der saugseitigen Deckscheibe 14. Der Durchmesser d der Öffnung 15 beträgt im Ausführungsbeispiel etwa die Hälfte des Durchmessers D des Laufrades 5.The
Der innere Abschnitt 13a der Schaufeln 13 ist schneckenförmig gekrümmt, jedoch in axiale Richtung frei von Überlappungen oder Überschneidungen, um eine einfache Entformbarkeit sicherzustellen. Im äußeren Abschnitt 13b besitzen die Schaufeln 13, abgesehen von eventuellen Gussschrägen, einen rechteckigen Querschnitt, der rechtwinkelig auf die saugseitige Deckscheibe 14 steht, um auch hier eine einfache Entformbarkeit zu sichern.The
Eine konvexe Oberfläche 16 der Schaufeln 13 erstreckt sich glattflächig vom inneren Abschnitt 13a zum äußeren Abschnitt 13b. Der konvexen Oberfläche 16 gegenüberliegend ist eine konkave Oberfläche 17 ausgebildet. In der konkaven Oberfläche 17 ist vom inneren Abschnitt 13a zum äußeren Abschnitt 13b eine Kante 18 ausgebildet, die gusstechnisch erforderlich ist. Die saugseitige Deckscheibe 14 ist im Übergang zur Öffnung 15 bei 20 verrundet, um eine optimale Strömungsumlenkung zu erreichen. Ein axialer Vorsprung 21 im Bereich der Öffnung 15 ermöglicht eine mögliche Strömungsoptimierung. Im äußeren Abschnitt 13b weisen die Schaufeln 13 an der Druckseite eine Stirnfläche 22 auf, die - zumindest teilweise - die Auflage für die druckseitige Deckscheibe 24 bildet. Die Stirnfläche 22 kann in einer zur Achse 5' des Laufrades 5 senkrechten Ebene liegen (
Die
Während in
Wie aus den
Mit dem beschriebenen erfindungsgemäßen Laufrad 5 können Pumpen mit äußerst hohem Wirkungsgrad kostengünstig hergestellt werden, der den Wirkungsgrad von Pumpen mit geschlossenen Laufrädern mit zweidimensionalen Schaufeln übertrifft. Dabei ist das Laufrad 5 aufgrund seiner einfachen Entformbarkeit gusstechnisch sehr leicht herzustellen. Überdies hat ein solches Laufrad 5 hervorragende Kavitationseigenschaften.With the described
Aufgrund der druckseitigen Deckscheibe eignet sich das erfindungsgemäße Laufrad 5 vorzüglich zum Umbau und zur Aufrüstung von Pumpen mit relativ großem Ringraum 25, ohne dass das Pumpengehäuse 2 getauscht oder verändert werden muss.Due to the pressure-side cover plate, the
Claims (8)
- An impeller (5) for a pump, in particular for a cooling water pump of an internal combustion engine, having an impeller body (5a) having a hub (11), a suction-side cover disk (14) having a central opening (15) for suctioning a delivery medium, and having at least one blade (13), which is integrally connected to the suction-side cover disk (14), and which has an inner section (13a) in the area of the central opening (15) and an outer section (13b) in the area of the suction-side cover disk (14), the blade (13) being implemented as three-dimensionally curved in the inner section (13a) and essentially two-dimensionally in the outer section (13b), the impeller (5) being produced in a casting method and each blade (13) being free of overlaps and undercuts, characterised in that the impeller (5) has a pressure-side cover disk (24), which is implemented as a separate part and is fixedly rotationally connected to the impeller body (5a), the pressure-side cover disk (24) has at least one grooved depression (26), which is shaped corresponding to the front face (22) and the profile of the blade (13), for the blade (13) for the positive connection thereto on the side (24a) facing toward the blade (13),.
- The impeller (5) according to claim 1, characterised in that the diameter of the pressure-side cover disk (24) at least corresponds to the diameter of an adjoining ring space (25), which is formed between the impeller shaft (4) and housing (1).
- The impeller (5) according to claim 1 or 2, characterised in that the diameter (d1) of the pressure-side cover disk (24) essentially corresponds to the diameter of a shaft seal (10), which delimits the ring space (25).
- The impeller (5) according to claim 1 or 2, characterised in that the diameter (d1) of the pressure-side cover disk (24) essentially corresponds to the diameter (d2) of the suction-side cover disk (14).
- The impeller (5) according to one of claims 1 through 4, characterised in that the pressure-side cover disk (24) is implemented as planar.
- The impeller (5) according to one of claims 1 through 4, characterised in that the pressure-side cover disk (24) is implemented as concavely curved on the side (24a) facing toward the blade (13).
- The impeller (5) according to one of claims 1 through 6, characterised in that each blade (13) is two-dimensionally curved and is perpendicular to the plane of the suction-side cover disk (14) in the area of the suction-side cover disk (14).
- The impeller (5) according to one of claims 1 through 7, characterised in that the wall thickness (s1) of the pressure-side cover disk (24) essentially corresponds to the wall thickness (s2) of the suction-side cover disk (24).
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
AT0011408A AT506342B1 (en) | 2008-01-25 | 2008-01-25 | WHEEL FOR A PUMP |
PCT/EP2009/050602 WO2009092711A1 (en) | 2008-01-25 | 2009-01-20 | Impeller for a pump |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2232080A1 EP2232080A1 (en) | 2010-09-29 |
EP2232080B1 true EP2232080B1 (en) | 2012-03-14 |
Family
ID=40513933
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP09703931A Not-in-force EP2232080B1 (en) | 2008-01-25 | 2009-01-20 | Impeller for a pump |
Country Status (5)
Country | Link |
---|---|
US (1) | US20100316497A1 (en) |
EP (1) | EP2232080B1 (en) |
AT (2) | AT506342B1 (en) |
BR (1) | BRPI0906780B1 (en) |
WO (1) | WO2009092711A1 (en) |
Families Citing this family (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102011012074A1 (en) * | 2011-02-23 | 2012-08-23 | Wilo Se | Running wheel for use in centrifugal pump, has blades arranged between front-side support plate and rear cover plate, which is welded as individual part at tubular shaft coaxial seat by ultrasonic welding process |
US20140030099A1 (en) * | 2012-07-27 | 2014-01-30 | GM Global Technology Operations LLC | Pump impeller |
DE102014201487B3 (en) * | 2014-01-28 | 2015-03-05 | Bühler Motor GmbH | The centrifugal pump impeller |
AT517163B1 (en) | 2015-05-13 | 2019-08-15 | Bitter Eng & Systemtechnik Gmbh | ROTARY PUMP |
US10584713B2 (en) | 2018-01-05 | 2020-03-10 | Spectrum Brands, Inc. | Impeller assembly for use in an aquarium filter pump and methods |
DE102020123517B4 (en) | 2020-09-09 | 2024-06-06 | Nidec Gpm Gmbh | Impeller for a centrifugal fluid pump and centrifugal fluid pump comprising the impeller and motor vehicle comprising such a centrifugal fluid pump |
Family Cites Families (16)
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 (en) | 1983-03-09 | 1984-09-19 | Kubota Ltd | Impeller of centrifugal pump |
ATE38708T1 (en) * | 1984-05-24 | 1988-12-15 | Moh 9 Proprietary Limited | IMPELLER FOR PUMP. |
DE3611910A1 (en) | 1986-04-09 | 1987-10-15 | Schaeffler Waelzlager Kg | IMPELLER FOR A RADIAL PUMP |
US4720242A (en) | 1987-03-23 | 1988-01-19 | Lowara, S.P.A. | Centrifugal pump impeller |
DE3731161C2 (en) * | 1987-09-17 | 1996-12-12 | Klein Schanzlin & Becker Ag | Centrifugal pump impeller |
DE3839190C1 (en) | 1988-11-18 | 1990-04-19 | Ksb Aktiengesellschaft, 6710 Frankenthal, De | |
DE4040200C2 (en) * | 1990-12-15 | 1994-11-17 | Freudenberg Carl Fa | Coolant pump for mounting on the pump housing of an internal combustion engine |
DE19742023B4 (en) | 1997-09-24 | 2006-07-13 | Beez, Günther, Dipl.-Ing. | Wheel |
DE10050108A1 (en) | 2000-10-09 | 2002-06-06 | Allweiler Ag | Rotor for turbine pump has bearing tube with bore to receive shaft and even number of vanes formed on it |
AT413872B (en) * | 2002-10-17 | 2006-06-15 | Bitter Engineering & Systemtec | WHEEL FOR A PUMP |
DE10354749A1 (en) | 2003-11-21 | 2005-06-23 | Siemens Ag | Method for producing an impeller for a centrifugal pump |
DE102005031589A1 (en) * | 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 |
-
2008
- 2008-01-25 AT AT0011408A patent/AT506342B1/en not_active IP Right Cessation
-
2009
- 2009-01-20 AT AT09703931T patent/ATE549517T1/en active
- 2009-01-20 US US12/735,522 patent/US20100316497A1/en not_active Abandoned
- 2009-01-20 BR BRPI0906780-9A patent/BRPI0906780B1/en not_active IP Right Cessation
- 2009-01-20 WO PCT/EP2009/050602 patent/WO2009092711A1/en active Application Filing
- 2009-01-20 EP EP09703931A patent/EP2232080B1/en not_active Not-in-force
Also Published As
Publication number | Publication date |
---|---|
ATE549517T1 (en) | 2012-03-15 |
AT506342B1 (en) | 2011-03-15 |
BRPI0906780A2 (en) | 2015-07-14 |
WO2009092711A1 (en) | 2009-07-30 |
BRPI0906780B1 (en) | 2020-03-31 |
AT506342A1 (en) | 2009-08-15 |
EP2232080A1 (en) | 2010-09-29 |
US20100316497A1 (en) | 2010-12-16 |
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