EP0369268B1 - Impeller for turbo machines - Google Patents

Impeller for turbo machines Download PDF

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Publication number
EP0369268B1
EP0369268B1 EP89120438A EP89120438A EP0369268B1 EP 0369268 B1 EP0369268 B1 EP 0369268B1 EP 89120438 A EP89120438 A EP 89120438A EP 89120438 A EP89120438 A EP 89120438A EP 0369268 B1 EP0369268 B1 EP 0369268B1
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EP
European Patent Office
Prior art keywords
impeller
ring element
cover plate
parts
hub
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
EP89120438A
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German (de)
French (fr)
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EP0369268A3 (en
EP0369268A2 (en
Inventor
Axel Riel
Primo Lovisetto
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KSB AG
Original Assignee
KSB AG
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Publication date
Application filed by KSB AG filed Critical KSB AG
Priority to AT89120438T priority Critical patent/ATE84852T1/en
Publication of EP0369268A2 publication Critical patent/EP0369268A2/en
Publication of EP0369268A3 publication Critical patent/EP0369268A3/en
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Publication of EP0369268B1 publication Critical patent/EP0369268B1/en
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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
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D5/00—Blades; Blade-carrying members; Heating, heat-insulating, cooling or antivibration means on the blades or the members
    • F01D5/02—Blade-carrying members, e.g. rotors
    • F01D5/025—Fixing blade carrying members on shafts
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2230/00—Manufacture
    • F05D2230/50—Building or constructing in particular ways
    • F05D2230/54—Building or constructing in particular ways by sheet metal manufacturing

Definitions

  • the invention relates to an impeller according to the preamble of the main claim.
  • US-A 2 344 444 shows an impeller on the hub of which U-shaped blade channels are arranged in a radial direction in the radial direction and are connected to a radially extending pressure-side impeller cover disk.
  • This solution may have sufficient strength, but due to the shape of the blade used, the flow properties are disadvantageous.
  • DE-B 1 703 266 shows a solution common in small heating circulating pumps, according to which a frictional connection between a pressure-side impeller hub acting as a hub and a conical part on the pump shaft is provided.
  • WO 86/06799 shows a solution in which the pressure-side impeller cover disk is pressed against the impeller hub with an impeller fastening nut.
  • the object of the invention is to develop a construction for impellers of turbomachines which are composed of several individual parts and which have a high fatigue strength without impairing the flow properties. This object is achieved in accordance with the characterizing part of the main claim.
  • the design according to the invention ensures that, on the one hand, attachment is carried out on the smallest possible radius, which is subject to little centrifugal force.
  • a major advantage is that hydraulic forces prevailing in the impeller inlet area can be introduced directly into the hub. This relieves the hydraulic forces of the connection between the beginning of the blade and the impeller cover plate on the pressure side. Furthermore, direct power transmission from the torque-introducing hub into the blades is possible. By means of the separation made in this way, tension within the impeller can be substantially avoided and a higher strength is the direct result.
  • An embodiment of the invention provides that an impeller fastening device presses the ring element or the ring element parts against the hub end face and / or the impeller cover disk on the pressure side located in this area. With the help of the impeller attachment device a safe Pressure or fastening of the loaded blade parts in the hub area guaranteed. This measure, which serves to simplify production, allows prefabrication of the parts to be joined and results in easier impeller assembly.
  • an embodiment of the invention provides that a pressure element is attached to the ring element or to the parts forming a ring element. Furthermore, another embodiment of the invention provides that the ring element, the ring element parts or the pressure element are designed to transmit torque. This reliably prevents the blade beginnings from being overstressed due to bending forces. As a result of the direct introduction of force into the blades or into the blade feet, there is no risk of overloading the connection between the blades or the blade feet and the impeller cover disk on the pressure side.
  • the force can be introduced here by a known tongue and groove connection, splined shaft or the like.
  • impeller fastening device which can be designed as a nut, for example, from twisting between the blade and the impeller cover plate on the pressure side when tightened. Also, no relative rotation between the blades and the impeller cover plate on the pressure side can take place during operation.
  • a further embodiment of the invention provides that the pressure-side impeller cover disk, the ring element or the ring element parts and / or the pressure element are arranged in a materially bonded, glued, frictional or positive manner in the area of the hub end face.
  • Appropriate welded connections or pressing the ring element or the ring element parts into a correspondingly shaped hub end face ensures a secure transmission of forces between the individual parts.
  • Another embodiment shows that in the case of hubs whose outer diameter is greater than the diameter in the fastening area between the hub end face and the pressure-side impeller cover disk, in the larger diameter area there is a free space between the hub and the pressure-side impeller cover disk.
  • an impeller (1) radial design is shown, which is mounted on a shaft (2).
  • a force is introduced from the shaft into a hub (4) via a tongue and groove connection (3), to the hub end face (5) of which a pressure-side impeller cover plate (6) is fastened by means of a welded connection (7).
  • a hub disk (8) supports the impeller cover disk (6) on the pressure side with respect to the hub (4), the parts here also being held together using welding technology.
  • the impeller cover disk (6) on the pressure side is connected to the hub (4) only in the area of the welded joint (7).
  • a region of the hub end face (5) which is located on a larger diameter and which is downstream of the welded connection has a free space (9) in order to rule out contact and thus tension between the parts.
  • the larger hub outer diameter may be necessary in those cases in which a large torque has to be transmitted from the shaft.
  • each blade (10) is provided with a ring element part (11), as shown in FIGS. 6 and 7, and is therefore welded to the hub end face (5).
  • An impeller fastening device (12) presses a pressure element (13) which is in engagement with the tongue and groove connection (3) and the parts arranged on the hub end face.
  • the hub is supported on a shaft shoulder (14).
  • the hub end face (5) is rounded in this exemplary embodiment and has a design which additionally ensures a positive connection with the ring element parts (11) attached to the blades.
  • a connection in this case a welded connection (15), takes place between the blades (10) and the impeller cover disk (6) on the pressure side, in the region of a plane which is perpendicular or almost perpendicular to the pump shaft (2). This eliminates tension in the curved blade area.
  • the impeller cover disk (16) on the suction side and a suction mouth (17) are fastened to the blades (10).
  • FIG. 2 shows a variant in which the ring element parts (11) are connected to the pressure element (13), and these parts are pressed by the impeller fastening device (12) against the hub end face (5) which runs flat here. Furthermore, the pressure element (13) has a projection (18) with which it is guided in the hub (4).
  • the ring element parts (11) are connected to the hub face (5) and the pressure element (13) to the ring element parts (11).
  • other connection options are also conceivable.
  • the pressure element (13) and the ring element parts (11) are between the hub end face (5) and the pressure-side impeller cover disk (6).
  • the impeller fastening device (12) then presses the pressure element (13) and ring element parts (11) against the pressure-side impeller cover plate (6).
  • a tongue and groove connection (3) guides the torque to be transmitted into the impeller.
  • a transmission by means of a splined shaft or the like is also possible.
  • FIG. 5 shows that instead of ring element parts that can be attached to the blade, a ring element (19) designed and shown as a separate part can be connected to the blades.
  • a ring element (19) designed and shown as a separate part can be connected to the blades.
  • an adhesive connection or a positive connection there is also the possibility of an adhesive connection or a positive connection. It is therefore readily possible to replace the ring element parts (11) by the ring element (19) in the exemplary embodiments in FIGS. 1 to 4.
  • FIG. 6 shows a perspective view of an individual blade (10), which here has a Z-shaped cross section and on the blade root (20) of which a ring element part (11) is directly molded.
  • the ring element (19) can be connected directly to the blade root (20) by an appropriate design or connection.
  • the bore shown serves as a relief bore for the axial thrust.
  • the top view of the impeller shown in FIG. 7 shows the arrangement of the individual blades (10) and how the individual ring element parts (11) form a ring after assembly.
  • the torque introduced through the tongue and groove connection (3) is transferred evenly and directly to the blades (10). Unfavorable tension can thus be avoided.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Recrystallisation Techniques (AREA)

Abstract

The invention relates to an impeller composed of a plurality of individual parts, the blades (10) of which impeller are fixed directly in the end face region (5) of an impeller boss (4) with the aid of an annular element (19) or of annular element parts (11) attached to the individual blades (10) (Fig. 1). <IMAGE>

Description

Die Erfindung betrifft ein Laufrad gemäß dem Oberbegriff des Hauptanspruches.The invention relates to an impeller according to the preamble of the main claim.

Bei aus Blechteilen gefertigten Laufrädern finden unterschiedliche Methoden Anwendung, um eine Kräfteübertragung zwischen der Welle und dem Laufrad mit seinen Schaufeln sicherzustellen. So ist es aus der US-A 3 025 069 bekannt, an einer Nabe eine druckseitige Laufraddeckscheibe sowie eine daran anliegende Nabenscheibe anzubringen. Dabei hält eine Wellenmutter unter Zwischenschaltung einer Unterlegscheibe die Nabe auf der Pumpenwelle fest. Wie die Verbindung zwischen der druckseitigen Laufraddeckscheibe mit der Nabe, mit den einzelnen Schaufeln sowie der saugseitigen Laufraddeckscheibe erfolgt, ist dieser Schrift jedoch nicht entnehmbar, vermutlich jedoch mittels Schweißtechnik.In the case of impellers made from sheet metal parts, different methods are used to ensure the transmission of forces between the shaft and the impeller with its blades. It is known from US Pat. No. 3,025,069 to attach a pressure-side impeller cover disk and a hub disk lying thereon to a hub. A shaft nut holds the hub on the pump shaft with the interposition of a washer. How the connection between the pressure-side impeller cover disc with the hub, with the individual blades and the suction-side impeller cover disc is made, however, is not apparent from this document, but probably by welding technology.

Die US-A 2 344 444 zeigt ein Laufrad, auf dessen Nabe U-förmig gebogene Schaufelkanäle in radialer Richtung strahlenförmig angeordnet und mit einer sich radial erstreckenden druckseitigen Laufraddeckscheibe verbunden sind. Diese Lösung mag zwar eine ausreichende Festigkeit aufweisen, jedoch infolge der verwendeten Schaufelform sind die strömungstechnischen Eigenschaften nachteiliger Art.US-A 2 344 444 shows an impeller on the hub of which U-shaped blade channels are arranged in a radial direction in the radial direction and are connected to a radially extending pressure-side impeller cover disk. This solution may have sufficient strength, but due to the shape of the blade used, the flow properties are disadvantageous.

Durch die US-A 2 360 440 ist bekannt, die druckseitige Laufraddeckscheibe unter Zwischenschaltung von Verstärkungselementen mit der Laufradnabe zu vernieten und die Schaufeln mit den Deckscheiben zu verschweißen. Die DE-B 1 703 266 zeigt eine bei kleinen Heizungsumwälzpumpen gebräuchliche Lösung, derzufolge eine reibschlüssige Befestigung zwischen einer als Nabe wirkenden druckseitigen Laufradnabe und einem konisch ausgebildeten Teil auf der Pumpenwelle vorsieht.From US-A 2 360 440 it is known to rivet the pressure-side impeller cover disk with the interposition of reinforcing elements to the impeller hub and to weld the blades to the cover disks. DE-B 1 703 266 shows a solution common in small heating circulating pumps, according to which a frictional connection between a pressure-side impeller hub acting as a hub and a conical part on the pump shaft is provided.

Die WO 86/06799 zeigt eine Lösung, bei der die druckseitige Laufraddeckscheibe mit einer Laufradbefestigungsmutter an die Laufradnabe gepreßt wird.WO 86/06799 shows a solution in which the pressure-side impeller cover disk is pressed against the impeller hub with an impeller fastening nut.

Der Erfindung liegt die Aufgabe zugrunde, für aus mehreren Einzelteilen zusammengesetzte Laufräder von Strömungsmaschinen eine Konstruktion zu entwickeln, welche ohne Beeinträchtigung der strömungstechnischen Eigenschaften eine hohe Dauerfestigkeit aufweist. Die Lösung dieser Aufgabe erfolgt gemäß dem kennzeichnenden Teil des Hauptanspruches.The object of the invention is to develop a construction for impellers of turbomachines which are composed of several individual parts and which have a high fatigue strength without impairing the flow properties. This object is achieved in accordance with the characterizing part of the main claim.

Durch die erfindungsgemäße Ausbildung wird sichergestellt, daß zum einen auf kleinstmöglichem Radius eine durch Fliehkräfte wenig belastete Befestigung erfolgt. Ein wesentliche Vorteil besteht darin, daß im Laufradeintrittsbereich vorherrschende hydraulische Kräfte direkt in die Nabe eingeleitet werden können. Somit wird die Verbindung zwischen Schaufelanfang und druckseitiger Laufraddeckscheibe von den hydraulischen Kräften entlastet. Desweiteren ist eine direkte Kraftübertragung von der Drehmomente einleitenden Nabe in die Schaufeln möglich. Mittels der so vorgenommenen Trennung lassen sich Verspannungen innerhalb des Laufrades im wesentlichen Umfang vermeiden und eine höhere Festigkeit ist die direkte Folge.The design according to the invention ensures that, on the one hand, attachment is carried out on the smallest possible radius, which is subject to little centrifugal force. A major advantage is that hydraulic forces prevailing in the impeller inlet area can be introduced directly into the hub. This relieves the hydraulic forces of the connection between the beginning of the blade and the impeller cover plate on the pressure side. Furthermore, direct power transmission from the torque-introducing hub into the blades is possible. By means of the separation made in this way, tension within the impeller can be substantially avoided and a higher strength is the direct result.

Eine Ausgestaltung der Erfindung sieht vor, daß eine Laufradbefestigungseinrichtung das Ringelement oder die Ringelementteile gegen die Nabenstirnseite und/oder die in diesem Bereich befindliche druckseitige Laufraddeckscheibe preßt. Mit Hilfe der Laufradbefestigungseinrichtung wird eine sichere Anpressung bzw. Befestigung der belasteten Schaufelteile im Nabenbereich gewährleistet. Diese der Fertigungsvereinfachung dienende Maßnahme erlaubt eine Vorfertigung der zu fügenden Teile und ergibt eine einfachere Laufradmontage.An embodiment of the invention provides that an impeller fastening device presses the ring element or the ring element parts against the hub end face and / or the impeller cover disk on the pressure side located in this area. With the help of the impeller attachment device a safe Pressure or fastening of the loaded blade parts in the hub area guaranteed. This measure, which serves to simplify production, allows prefabrication of the parts to be joined and results in easier impeller assembly.

Zur besseren Krafteinleitung von der Welle in das Laufrad sieht eine Ausgestaltung der Erfindung vor, daß an dem Ringelement oder an den ein Ringelement bildenden Teilen ein Druckelement angebracht ist. Desweiteren sieht eine andere Ausgestaltung der Erfindung vor, daß das Ringelement, die Ringelementteile oder das Druckelement drehmomentübertragend gestaltet sind. Damit wird in zuverlässiger Weise eine durch Biegekräfte bedingte Überanspruchung der Schaufelanfänge ausgeschlossen. Infolge der direkten Krafteinleitung in die Schaufeln bzw. in die Schaufelfüße besteht keine Gefahr einer Überlastung der Verbindung zwischen den Schaufeln bzw. den Schaufelfüßen und druckseitiger Laufraddeckscheibe. Die Krafteinleitung kann hier durch eine bekannte Nut-Feder-Verbindung, Vielkeilwelle oder dgl. erfolgen. Dies verhindert weiterhin, daß die Laufradbefestigungseinrichtung, welche beispielsweise als Mutter ausgebildet sein kann, beim Festdrehen eine Verdrehung zwischen Schaufel und druckseitiger Laufraddeckscheibe bewirkt. Auch kann während des Betriebes keine Relativverdrehung zwischen den Schaufeln und der druckseitigen Laufraddeckscheibe erfolgten.For better introduction of force from the shaft into the impeller, an embodiment of the invention provides that a pressure element is attached to the ring element or to the parts forming a ring element. Furthermore, another embodiment of the invention provides that the ring element, the ring element parts or the pressure element are designed to transmit torque. This reliably prevents the blade beginnings from being overstressed due to bending forces. As a result of the direct introduction of force into the blades or into the blade feet, there is no risk of overloading the connection between the blades or the blade feet and the impeller cover disk on the pressure side. The force can be introduced here by a known tongue and groove connection, splined shaft or the like. This further prevents the impeller fastening device, which can be designed as a nut, for example, from twisting between the blade and the impeller cover plate on the pressure side when tightened. Also, no relative rotation between the blades and the impeller cover plate on the pressure side can take place during operation.

Eine weitere Ausgestaltung der Erfindung sieht vor, daß im Bereich der Nabenstirnseite die druckseitige Laufraddeckscheibe, das Ringelement oder die Ringelementteile und/oder das Druckelement stoffschlüssig, geklebt, reibschlüssig oder formschlüssig angeordnet sind. Durch entsprechende Schweißverbindungen oder Einpressen des Ringelementes oder der Ringelementteile in eine entsprechend geformte Nabenstirnseite ist eine sichere Kräfteübertragung zwischen den Einzelteilen gewährleistet.A further embodiment of the invention provides that the pressure-side impeller cover disk, the ring element or the ring element parts and / or the pressure element are arranged in a materially bonded, glued, frictional or positive manner in the area of the hub end face. Appropriate welded connections or pressing the ring element or the ring element parts into a correspondingly shaped hub end face ensures a secure transmission of forces between the individual parts.

Eine andere Ausgestaltung zeigt, daß bei Naben, deren Außendurchmesser größer ist als der Durchmesser im Befestigungsbereich zwischen Nabenstirnseite und druckseitiger Laufraddeckscheibe, im größeren Durchmesserbereich mit einem Freiraum zwischen Nabe und druckseitiger Laufraddeckscheibe versehen sind.Another embodiment shows that in the case of hubs whose outer diameter is greater than the diameter in the fastening area between the hub end face and the pressure-side impeller cover disk, in the larger diameter area there is a free space between the hub and the pressure-side impeller cover disk.

Weiter zeigte es sich, daß die Ausgestaltung, nach der die Schaufeln an der druckseitigen Laufraddeckscheibe in senkrecht oder nahezu senkrecht auf der Pumpenwelle stehenden Ebene oder Ebenen befestigt sind, eine wesentliche Erhöhung der Dauerfestigkeit bedingt. Infolge der Vermeidung von Befestigungspunkten zwischen gekrümmten Teilen, beispielsweise durch Punktschweißen, werden unzulässige Spannungspitzen im Bereich dieser Verbindungspunkte ausgeschlossen. Das Anbringen der Schweißnähte in senkrecht oder nahezu senkrecht auf der Drehachse stehenden Ebenen gewährleistet ein hohes Maß an Betriebssicherheit.Furthermore, it was found that the design according to which the blades are attached to the pressure-side impeller cover plate in a plane or planes standing vertically or almost vertically on the pump shaft causes a substantial increase in the fatigue strength. As a result of avoiding fastening points between curved parts, for example by spot welding, impermissible voltage peaks in the area of these connection points are excluded. The application of the weld seams in planes standing vertically or almost vertically on the axis of rotation ensures a high degree of operational safety.

Ein Ausführungsbeispiel der Erfindung ist in den Zeichnungen dargestellt und wird im folgenden näher beschrieben. Es zeigen die

  • Fig.1 bis 4 verschiedene Befestigungsmöglichkeiten an im Schnitt dargestellten Laufrädern, die
  • Fig. 5 ein Ringelement und dessen Verbindung mit den Schaufeln, die
  • Fig. 6 eine Schaufel mit angeformtem Ringelementteil und die
  • Fig. 7 eine Draufsicht auf ein mit Teilen der Fig. 6 zusammengesetztes Laufrad.
An embodiment of the invention is shown in the drawings and will be described in more detail below. They show
  • Fig.1 to 4 different mounting options on wheels shown in section, the
  • Fig. 5 shows a ring element and its connection to the blades, the
  • Fig. 6 shows a blade with a molded ring element part and
  • Fig. 7 is a plan view of an impeller assembled with parts of Fig. 6.

In der Fig. 1 ist ein Laufrad (1) radialer Bauart dargestellt, welches auf einer Welle (2) montiert ist. Über eine Nut-Feder-Verbindung (3) erfolgt eine Krafteinleitung von der Welle in eine Nabe (4), an deren Nabenstirnseite (5) eine druckseitige Laufraddeckscheibe (6) mittels Schweißverbindung (7) befestigt ist. Zusätzlich stützt eine Nabenscheibe (8) die druckseitige Laufraddeckscheibe (6) gegenüber der Nabe (4) ab, wobei die Teile hier ebenfalls mittels Schweißtechnik zusammengehalten werden. Die druckseitige Laufraddeckscheibe (6) ist mit der Nabe (4) nur im Bereich der Schweißverbindung (7) verbunden. Ein auf größerem Durchmesser befindlicher und der Schweißverbindung nachgeordneter Bereich der Nabenstirnseite (5) weist einen Freiraum (9) auf, um eine Anlage und damit eine Verspannung zwischen den Teilen auszuschließen. Der größere Nabenaußendurchmesser kann in denjenigen Fällen notwendig sein, in denen von der Welle ein großes Drehmoment zu übertragen ist.In Fig. 1, an impeller (1) radial design is shown, which is mounted on a shaft (2). A force is introduced from the shaft into a hub (4) via a tongue and groove connection (3), to the hub end face (5) of which a pressure-side impeller cover plate (6) is fastened by means of a welded connection (7). In addition, a hub disk (8) supports the impeller cover disk (6) on the pressure side with respect to the hub (4), the parts here also being held together using welding technology. The impeller cover disk (6) on the pressure side is connected to the hub (4) only in the area of the welded joint (7). A region of the hub end face (5) which is located on a larger diameter and which is downstream of the welded connection has a free space (9) in order to rule out contact and thus tension between the parts. The larger hub outer diameter may be necessary in those cases in which a large torque has to be transmitted from the shaft.

Jede Schaufel (10) ist in diesem Ausführungsbeispiel mit einem - wie in den Fig. 6 und 7 gezeigt - Ringelementteil (11) versehen und damit an der Nabenstirnseite (5) verschweißt. Eine Laufradbefestigungseinrichtung (12) preßt ein Druckelement (13), welches mit der Nut-Feder-Verbindung (3) in Eingriff steht sowie die an der Nabenstirnseite angeordneten Teile zusammen. Hierbei stützt sich die Nabe an einer Wellenschulter (14) ab.In this exemplary embodiment, each blade (10) is provided with a ring element part (11), as shown in FIGS. 6 and 7, and is therefore welded to the hub end face (5). An impeller fastening device (12) presses a pressure element (13) which is in engagement with the tongue and groove connection (3) and the parts arranged on the hub end face. The hub is supported on a shaft shoulder (14).

Die Nabenstirnseite (5) ist in diesem Ausführungsbeispiel gerundet ausgebildet und weist eine Gestaltung auf, welche zusätzlich eine formschlüssige Verbindung mit den an den Schaufeln angebrachten Ringelementteilen (11) sicherstellt.The hub end face (5) is rounded in this exemplary embodiment and has a design which additionally ensures a positive connection with the ring element parts (11) attached to the blades.

Zwischen den Schaufeln (10) und der druckseitigen Laufraddeckscheibe (6) erfolgt eine Verbindung, hier eine Schweißverbindung (15), im Bereich einer senkrecht oder nahezu senkrecht auf der Pumpenwelle (2) stehenden Ebene. Somit werden Verspannungen in dem bogenförmig verlaufenden Schaufelbereich ausgeschlossen.A connection, in this case a welded connection (15), takes place between the blades (10) and the impeller cover disk (6) on the pressure side, in the region of a plane which is perpendicular or almost perpendicular to the pump shaft (2). This eliminates tension in the curved blade area.

An den Schaufeln (10) sind die saugseitige Laufraddeckscheibe (16) sowie ein Saugmund (17) befestigt.The impeller cover disk (16) on the suction side and a suction mouth (17) are fastened to the blades (10).

Die Ausgestaltung der Fig. 2 zeigt eine Variante, bei der die Ringelementteile (11) mit dem Druckelement (13) verbunden sind, und diese Teile von der Laufradbefestigungseinrichtung (12) gegen die hier plan verlaufende Nabenstirnseite (5) gepreßt werden. Desweiteren weist das Druckelement (13) einen Vorsprung (18) auf, mit dem es in der Nabe (4) geführt ist.The embodiment of FIG. 2 shows a variant in which the ring element parts (11) are connected to the pressure element (13), and these parts are pressed by the impeller fastening device (12) against the hub end face (5) which runs flat here. Furthermore, the pressure element (13) has a projection (18) with which it is guided in the hub (4).

Bei der Ausführungsform der Fig. 3 sind die Ringelementteile (11) mit der Nabenstirnseite (5) und dem Druckelement (13) mit den Ringelementteilen (11) verbunden. Neben den hier gezeigten Schweißverbindungen sind auch andere Möglichkeiten der Verbindung denkbar. Im Unterschied hierzu erfolgt bei dem Ausführungsbeispiel der Fig. 4 eine Verbindung zwischen dem Druckelement (13) und den Ringelementteilen (11) und zwischen der Nabenstirnseite (5) und der druckseitigen Laufraddeckscheibe (6). Die Laufradbefestigungseinrichtung (12) preßt dann Druckelement (13) und Ringelementteile (11) gegen die druckseitige Laufraddeckscheibe (6). Eine Nut-Feder-Verbindung (3) leitet auch in diesem Fall das zu übertragende Drehmoment in das Laufrad. Eine Übertragung mittels Vielkeilwelle oder dgl. ist ebenfalls möglich.In the embodiment of FIG. 3, the ring element parts (11) are connected to the hub face (5) and the pressure element (13) to the ring element parts (11). In addition to the welded connections shown here, other connection options are also conceivable. In contrast to this, in the exemplary embodiment in FIG. 4 there is a connection between the pressure element (13) and the ring element parts (11) and between the hub end face (5) and the pressure-side impeller cover disk (6). The impeller fastening device (12) then presses the pressure element (13) and ring element parts (11) against the pressure-side impeller cover plate (6). In this case too, a tongue and groove connection (3) guides the torque to be transmitted into the impeller. A transmission by means of a splined shaft or the like is also possible.

In der Fig. 5 ist gezeigt, daß anstelle an der Schaufel anbringbarer Ringelementteile ein als separates Teil ausgebildetes und gezeigtes Ringelement (19) mit den Schaufeln verbunden werden kann. Neben der hier gezeigten Möglichkeit, das Ringelement (19) an den Schaufeln anzuschweißen, besteht auch die Möglichkeit einer Klebeverbindung bzw. einer formschlüssigen Verbindung. Es ist also ohne weiteres möglich, bei den Ausführungsbeispielen der Fig. 1 bis 4 die Ringelementteile (11) durch das Ringelement (19) zu ersetzen.5 shows that instead of ring element parts that can be attached to the blade, a ring element (19) designed and shown as a separate part can be connected to the blades. In addition to the possibility shown here of welding the ring element (19) to the blades, there is also the possibility of an adhesive connection or a positive connection. It is therefore readily possible to replace the ring element parts (11) by the ring element (19) in the exemplary embodiments in FIGS. 1 to 4.

Die Fig. 6 zeigt als perspektivische Darstellung eine einzelne Schaufel (10), welche hier über einen Z-förmigen Querschnitt verfügt und an deren Schaufelfuß (20) ein Ringelementteil (11) direkt angeformt ist. Durch entsprechende Gestaltung oder Verbindung kann das Ringelement (19) direkt mit dem Schaufelfuß (20) verbunden werden. Die gezeigte Bohrung dient als Entlastungsbohrung für den Axialschub.6 shows a perspective view of an individual blade (10), which here has a Z-shaped cross section and on the blade root (20) of which a ring element part (11) is directly molded. The ring element (19) can be connected directly to the blade root (20) by an appropriate design or connection. The bore shown serves as a relief bore for the axial thrust.

In der in Fig. 7 gezeigten Draufsicht auf das Laufrad ist die Anordnung der einzelnen Schaufeln (10) erkennbar und wie die einzelnen Ringelementteile (11) nach der Montage einen Ring bilden. Das durch die Nut-Feder-Verbindung (3) eingeleitete Drehmoment wird gleichmäßig und direkt auf die Schaufeln (10) übertragen. Ungünstige Verspannungen können somit vermieden werden.The top view of the impeller shown in FIG. 7 shows the arrangement of the individual blades (10) and how the individual ring element parts (11) form a ring after assembly. The torque introduced through the tongue and groove connection (3) is transferred evenly and directly to the blades (10). Unfavorable tension can thus be avoided.

Claims (7)

  1. An impeller for fluid flow machines of the radial or semi-axial type, whose individual parts are fitted together as an integral impeller (1), a plurality of vanes (10) being arranged between a discharge side impeller cover plate (6), which is connected with a hub (4) for the transmission of force, and an intake side impeller cover plate (16) and the discharge side impeller cover plate (6) is connected with the hub end side (5) in a known manner, characterized in that a ring element (19) or ring element parts (11) connected with the vanes (10) are arranged on the hub end side (5) in a force transmitting manner.
  2. The impeller as claimed in claim 1, characterized in that an impeller attachment device (12) urges the ring element (19) or the ring element parts (11) against the hub end side (5) and/or the discharge side impeller cover plate (6) present here.
  3. The impeller as claimed in claim 1 and in claim 2, characterized in that a pressure element (13) is mounted on the ring element (19) or on the ring element parts (11) constituting a ring element.
  4. The impeller as claimed in any one of the claims 1 through 3, characterized in that the ring element (19), the ring element parts (11) and/or the pressure element (13) are designed for the transmission of torque.
  5. The impeller as claimed in any one of the claims 1 through 4, characterized in that adjacent to the hub end side (5) the discharge side impeller cover plate (6), the ring element (19) or the ring element parts (11) and/or the pressure element (13) are welded, bonded, frictionally joined or interlocked.
  6. The impeller as claimed in any one or more of the claims 1 through 5, characterized in that hubs, whose external diameter is greater than the diameter in the attachment zone between the hub end side (5) and the discharge side impeller cover plate (6) are provided in the major diameter part with a free space (9) between the hub end side (5) and the discharge side impeller cover plate (6).
  7. The impeller as claimed in any one or more of the claims 1 through 6, characterized in that the vanes (10) are mounted on the discharge side impeller cover plate (6) in a plane or planes which is or are perpendicular, or substantially so, to the pump shaft (2).
EP89120438A 1988-11-18 1989-11-04 Impeller for turbo machines Expired - Lifetime EP0369268B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT89120438T ATE84852T1 (en) 1988-11-18 1989-11-04 IMPELLER FOR TURBO MACHINES.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3839190 1988-11-18
DE3839190A DE3839190C1 (en) 1988-11-18 1988-11-18

Publications (3)

Publication Number Publication Date
EP0369268A2 EP0369268A2 (en) 1990-05-23
EP0369268A3 EP0369268A3 (en) 1990-08-29
EP0369268B1 true EP0369268B1 (en) 1993-01-20

Family

ID=6367511

Family Applications (1)

Application Number Title Priority Date Filing Date
EP89120438A Expired - Lifetime EP0369268B1 (en) 1988-11-18 1989-11-04 Impeller for turbo machines

Country Status (3)

Country Link
EP (1) EP0369268B1 (en)
AT (1) ATE84852T1 (en)
DE (1) DE3839190C1 (en)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT506342B1 (en) 2008-01-25 2011-03-15 Bitter Engineering & Systemtechnik Gmbh WHEEL FOR A PUMP

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2344444A (en) * 1940-03-29 1944-03-14 Malczewski Jeremi Construction of turbomachines
US2360440A (en) * 1942-01-26 1944-10-17 Evans Prod Co Rotary air impeller
US2882829A (en) * 1956-02-09 1959-04-21 Fmc Corp Fabricated impeller for pumps
US3025069A (en) * 1957-01-14 1962-03-13 Bell & Gossett Co Seat for rotary mechanical seals
DK132807C (en) * 1967-05-05 1976-07-12 Grundfos As BAG PUMP, ISER CIRCULATION PUMP FOR CENTRAL HEATING SYSTEM
DE3517499A1 (en) * 1985-05-15 1986-11-20 Klein, Schanzlin & Becker Ag, 6710 Frankenthal WHEEL
US4720242A (en) * 1987-03-23 1988-01-19 Lowara, S.P.A. Centrifugal pump impeller

Also Published As

Publication number Publication date
EP0369268A3 (en) 1990-08-29
ATE84852T1 (en) 1993-02-15
EP0369268A2 (en) 1990-05-23
DE3839190C1 (en) 1990-04-19

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