EP0723631A1 - Centrifugal pump, especially for fountains - Google Patents

Centrifugal pump, especially for fountains

Info

Publication number
EP0723631A1
EP0723631A1 EP95926885A EP95926885A EP0723631A1 EP 0723631 A1 EP0723631 A1 EP 0723631A1 EP 95926885 A EP95926885 A EP 95926885A EP 95926885 A EP95926885 A EP 95926885A EP 0723631 A1 EP0723631 A1 EP 0723631A1
Authority
EP
European Patent Office
Prior art keywords
impeller
centrifugal pump
pump according
impeller blades
rotor
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
EP95926885A
Other languages
German (de)
French (fr)
Other versions
EP0723631B1 (en
Inventor
Dieter Hoffmeier
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.)
*OASE G.M.B.H. & CO. K.G.
Original Assignee
Oase Pumpen Wuebker Soehne GmbH and Co Maschinenfabrik
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Oase Pumpen Wuebker Soehne GmbH and Co Maschinenfabrik filed Critical Oase Pumpen Wuebker Soehne GmbH and Co Maschinenfabrik
Publication of EP0723631A1 publication Critical patent/EP0723631A1/en
Application granted granted Critical
Publication of EP0723631B1 publication Critical patent/EP0723631B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

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
    • F04D13/00—Pumping installations or systems
    • F04D13/02—Units comprising pumps and their driving means
    • F04D13/021—Units comprising pumps and their driving means containing a coupling
    • 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
    • F04D29/247—Vanes elastic or self-adjusting

Definitions

  • the invention relates to a centrifugal pump, in particular for fountains and aquariums, according to the preamble of claim 1.
  • Known pumps of this type are equipped with a single-phase synchronous electric motor with a rotating field-generating auxiliary winding in the stator, which ensures a start-up in the predetermined direction of rotation.
  • a direction-dependent impeller can also be used.
  • With helical impeller blades a higher hydraulic efficiency can be achieved compared to an impeller that is independent of the direction of rotation with radially extending impeller blades.
  • the object of the invention is therefore to create a centrifugal pump which is characterized by simple and inexpensive production and which creates a compact and robust design without significant losses in overall efficiency.
  • the solution according to the invention according to claim 1 provides to use a single-phase synchronous motor with permanent magnet rotor without additional auxiliary winding as the drive and to determine the starting direction of such a motor by the reaction of the impeller. This is made possible with the trick of making the spiral impeller blades elastic and resilient in such a way that when the single-phase synchronous motor starts, they spread out in radial length in the opposite direction to the predetermined direction of rotation of the spiral impeller.
  • the invention provides that the impeller itself selects the "correct” direction of rotation. If the engine runs against the correct one first
  • Fig. 2 top view of the motor and impeller
  • FIG. 4 side view of the rotor and impeller
  • ORIGINAL DOCUMENTS 6 shows a further embodiment of an impeller in a sectional view corresponding to FIGS. 5 and
  • Fig. 7 view of a third embodiment of a
  • Impeller in a sectional view corresponding to FIGS. 5 and 6 together with an associated pump housing.
  • the centrifugal pump shown as a whole in longitudinal section in FIG. 1 and labeled 1 comprises a single-phase induction motor 2 with an external stator 3 and an internal rotatably mounted permanent magnet rotor 4, which is axially connected to an impeller 5 of a pump part 6 and between two bearings , namely a motor-side plug-in bearing 7 and a pump-side plug-in bearing 8.
  • the latter is held in a spiral housing 9 of the pump part 6, specifically centrally in an axial inlet in the form of a suction channel 10, through which the liquid to be pumped, for example the water of a fountain, is centrifuged by means of the impeller 5 to an outlet in the form of a pressure nozzle 11 is moved, which is designed with a slightly conical widening in a diffuser manner, in order to recover a higher pressure from the flow energy of the liquid in the pump with as little loss as possible.
  • the electric motor 2 of the centrifugal pump is a single-phase synchronous motor, the permanent magnet rotor being used to transfer current to the rotor and thus to brushes, slip rings and commutators
  • this embodiment of a single-phase induction motor is not only extremely safe electrically, but also installation-friendly with regard to centrifugal pumps, since the rotor 4 and the impeller 5 can be inserted from the open side of the can 12 facing the pump part 6 then also place the volute casing in the axial direction.
  • the housing in plastic with the possibility of using largely screw-free connections, in particular the possibility of plug-in and snap-in connections, this results in extremely easy and quick installation.
  • stator 3 comprises a laminated core 14 in a U-shape with two elongated legs 15, 16, each of which carries one winding half 17, 18 of the motor winding and one end encompass substantially cylindrical opening, within which (the can 12, not shown) and the rotor 4 is located. From Fig. 3
  • the laminated core 14 does not surround the rotor with axially circular cylindrical pole shoe surfaces, but rather with regions 19, 20 opposite one another, but arranged asymmetrically to the laminated core, creates a magnetic gap which forms an edge position with respect to the pole shoe shape of the legs 15, 16 emphasizes.
  • This has proven itself in relation to the inherently critical start-up of the single-phase induction motor, since the permanent magnet rotor aligns asymmetrically at rest and lies outside of the indifferent central position when switched on. This results in a generally easier starting of the rotor.
  • a certain direction of rotation of the motor is absolutely necessary in relation to a design of the pump part which is dependent on the direction of rotation and with direction-related coordination of the impeller 5 and the spiral housing 9.
  • Safety in this regard is provided according to the invention by the impeller 5, which is equipped with impeller blades 21 which spread out elastically against the specified direction of rotation when the synchronous motor starts up "incorrectly".
  • the deformation which is conventionally not desired in the case of such impellers can be structurally predetermined by a general elasticity of the material and / or by a specific cross-sectional configuration of the impeller blades, in particular with respect to a central region near a hub 22.
  • a lock against a "wrong" start can in principle already be achieved in that the impeller which spreads during reverse running forms a flow resistance in which the
  • the impeller can also be designed with respect to the spiral housing 9 such that the ends of the impeller blades when spreading due to the wrong running direction with a circumferential inner wall 23 of the spiral housing or also with stationary parts projecting inwards thereon, for example meet with rib-like or fin-like stops 24.
  • the latter is illustrated in FIG. 7 with a representation of the impeller, in which, in addition to the hatched area of an impeller 25 in broken lines, the spread shape of the impeller 25 when running in reverse and the shape of the impeller blades correspondingly curved in relation to the rest position are shown during forward running.
  • impeller blades from about 2% radial length, i.e. the (radial) distance of the ends of the impeller blades from the associated axis can already increase the flow resistance in reverse so much that the driving single-phase induction motor does not achieve a synchronous start. Such a limited spreading can also suffice to bring the impeller blades together with the stops and thus to stop a "wrong" start-up.
  • the impeller blades are preferably designed for a spread of 5 to 10% when running in reverse.
  • impeller blades creates not only effects dependent on the direction of rotation, but also load-dependent effects. While known impeller blades with a rigid sickle shape (at the fixed, predetermined synchronous speed) only perform well and offer good efficiency in a very limited middle range of head and throughput, the impeller blades, which are designed according to the invention, achieve over head and Throughput wide work areas with good performance and high efficiency. Moreover, unlike conventional pumps, the power requested and to be applied by the synchronous motor is over the entire range, i.e.
  • the torque transmission between rotor 4 and impeller 5 can take place with the aid of a one-way clutch, in which a coaxial assignment of a stub shaft 31 and a driving sleeve 32 are brought together in a latching manner, the driving sleeve 32 as far as is freely rotatable relative to the shaft 31 over an angular range, here of more than 120 ° on both sides, until a driver lug 33 on the sleeve 32 on one side or the other meets a driver stop 34 which is connected to the shaft 31 circulates.
  • the freewheel created in this way can be useful in many cases to facilitate the delicate start of the single-phase induction motor, since it is not under load

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Acyclic And Carbocyclic Compounds In Medicinal Compositions (AREA)
  • Pharmaceuticals Containing Other Organic And Inorganic Compounds (AREA)

Abstract

PCT No. PCT/EP95/02770 Sec. 371 Date Mar. 13, 1996 Sec. 102(e) Date Mar. 13, 1996 PCT Filed Jul. 14, 1995 PCT Pub. No. WO96/02763 PCT Pub. Date Feb. 1, 1996A centrifugal pump, particularly for fountains and aquariums, for which an electric motor and a pump are disposed coaxially to one another, the electric motor being constructed as a single-phase synchronous motor with a permanent magnet rotor and connected with an open impeller of the pump with impeller blades, which are bent back from a hub towards the outside spirally with respect to a specified direction of rotation, is improved in the direction of a simple and inexpensive production as well as a compact and robust construction without a significant loss in overall efficiency owing to the fact that the impeller blades are constructed flexibly in such a manner that, if the synchronous motor starts counter to the specified direction of rotation, they are propped open by at least 2% in the radial length.

Description

Kreiselpumpe, insbesondere für Springbrunnen Centrifugal pump, especially for fountains
Die Erfindung betrifft eine Kreiselpumpe, insbesondere für Spring¬ brunnen und Aquarien, nach dem Oberbegriff des Anspruchs 1.The invention relates to a centrifugal pump, in particular for fountains and aquariums, according to the preamble of claim 1.
Bekannte Pumpen dieser Art sind mit einem Einphasen-Synchron- elektromotor mit einer drehfelderzeugenden Hilfswicklung im Stator ausgestattet, die für einen Anlauf in der fest vorgegebenen Drehrich¬ tung sorgt. Indem motorseitig eine vorgegebene Drehrichtung ge¬ währleistet wird, kann auch ein drehrichtungsabhängiges Laufrad eingesetzt werden. Mit spiralförmigen Laufradschaufeln kann im Vergleich zu einem drehrichtungsunabhängigen Laufrad mit radial erstreckten Laufradschaufeln ein höherer hydraulischer Wirkungsgrad erreicht werden. Die laufradseitig erzielten Vorteile, die sich in der erforderiichen Motorleistung, den Fertigungskosten und der Baugröße niederschlagen, werden allerdings zum Teil durch denKnown pumps of this type are equipped with a single-phase synchronous electric motor with a rotating field-generating auxiliary winding in the stator, which ensures a start-up in the predetermined direction of rotation. By ensuring a predetermined direction of rotation on the motor side, a direction-dependent impeller can also be used. With helical impeller blades, a higher hydraulic efficiency can be achieved compared to an impeller that is independent of the direction of rotation with radially extending impeller blades. The advantages achieved on the impeller side, which are reflected in the required motor power, the manufacturing costs and the size, are, however, partly due to the
ORIGINAL UNTERLAGEN Aufwand für einen Hilfswick jngskreis im Stator aufgehoben j.id ins¬ besondere im Bereich kleiner Pumpen für den Gebrauch im Haus¬ und Gartenbereich ist nicht nur die Anschlußmöglichkeit an einen einphasigen Netzanschluß, sondern auch die in Zwang zu einer äußerst kostengünstigen, und kompakten Bauweise zu berücksichti¬ gen.ORIGINAL DOCUMENTS Effort for an auxiliary winding circuit in the stator is eliminated. Especially in the area of small pumps for use in the home and garden, not only is it possible to connect to a single-phase mains connection, but also in an extremely cost-effective and compact design take into account.
Aufgabe der Erfindung ist es daher, eine Kreiselpumpe zu schaffen, die sich durch eine einfache und preiswerte Fertigung auszeichnet und eine kompakte und robuste Ausführung ohne wesentliche Ein¬ bußen im Gesamtwirkungsgrad schafft.The object of the invention is therefore to create a centrifugal pump which is characterized by simple and inexpensive production and which creates a compact and robust design without significant losses in overall efficiency.
Die erfindungsgemäße Lösung nach Anspruch 1 sieht vor, als Antrieb einen Einphasen-Synchronmotor mit Permanentmagnetrotor ohne zusätzliche Hilfswicklung zu verwenden und die Anlaufrichtung eines solchen Motors durch die Reaktion des Laufrades festzulegen. Dies wird mit dem Kunstgriff ermöglicht, die spiralförmigen Laufrad¬ schaufeln in der Weise elastisch-federnd auszubilden, so daß sie sich beim Anlaufen des Einphasen-Synchronmotors in Gegenrichtung zur vorgegebenen Drehrichtung des spiralförmigen Laufrades in radialer Länge aufspreizen. Da einerseits bei einem solchen Einphasen- Synchronmotor die Drehrichtung des Läufers anlaufbedingt "offen" ist, andererseits bei einem spiralförmig ausgebildeten Laufrad nur dann ein brauchbarer hydraulischer Wirkungsgrad erzielt werden kann, wenn die "richtige" Drehrichtung des Laufrades eingehalten wird, sieht die Erfindung vor, daß das Laufrad selbst die "richtige" Drehrichtung auswählt. Läuft der Motor zunächst gegen die richtigeThe solution according to the invention according to claim 1 provides to use a single-phase synchronous motor with permanent magnet rotor without additional auxiliary winding as the drive and to determine the starting direction of such a motor by the reaction of the impeller. This is made possible with the trick of making the spiral impeller blades elastic and resilient in such a way that when the single-phase synchronous motor starts, they spread out in radial length in the opposite direction to the predetermined direction of rotation of the spiral impeller. Since, on the one hand, with such a single-phase synchronous motor, the direction of rotation of the rotor is "open" due to the start-up, and on the other hand, a usable hydraulic efficiency can only be achieved with a spiral-shaped impeller if the "correct" direction of rotation of the impeller is observed, the invention provides that the impeller itself selects the "correct" direction of rotation. If the engine runs against the correct one first
ORIGINAL UNTERLAGEN Drehrichtung an oder pendelt er irr Anlaut gsgen die richtige Dreh¬ richtung, so stellen sich die Laufradschaufeln auf, wodurch der Was¬ serwiderstand wesentlich erhöht und der Motor abgebremst wird. Mit der Tendenz des Einphasen-Synchronmotors zum Anlauf-Pendeln und der vom Laufrad bestimmten Vorzugsrichtung wird der Motor gezwungen, in der richtigen Drehrichtung anzulaufen.ORIGINAL DOCUMENTS Direction of rotation or if it starts to swing in the correct direction, the impeller blades rise, which considerably increases the water resistance and brakes the motor. With the tendency of the single-phase synchronous motor to start-up oscillation and the preferred direction determined by the impeller, the motor is forced to start in the correct direction of rotation.
Weitere Einzelheiten und Vorteile der Erfindung ergeben sich aus der nachfolgenden Beschreibung und der Zeichnung. In der Zeichnung zeigen:Further details and advantages of the invention result from the following description and the drawing. The drawing shows:
Fig. 1 Längsschnitt durch eine Kreiselpumpe,1 longitudinal section through a centrifugal pump,
Fig. 2 Draufsicht auf Motor und Pumpenrad derFig. 2 top view of the motor and impeller
Kreiselpumpe nach Fig 1 (ohne Motor- und Pumpengehäuse),Centrifugal pump according to Fig 1 (without motor and pump housing),
Fig. 3 (Schnitt-) Ansicht nach Linie lll-lll in Fig. 2,3 (sectional) view along line III-III in FIG. 2,
Fig. 4 Seitenansicht von Rotor und Laufrad derFig. 4 side view of the rotor and impeller
Kreiselpumpe gemäß Fig. 1 bis 3, in axial aus¬ einandergezogener Zuordnung,Centrifugal pump according to FIGS. 1 to 3, in axially pulled apart assignment,
Fig. 5 Schnitt nach Linie V-V in Fig. 4,5 section along line V-V in Fig. 4,
ORIGINAL UNTERLAGEN Fig. 6 eine weitere Λusführungsfcrm eines Laufrades in einer Schnittansicht entsprechend der Fig.5 undORIGINAL DOCUMENTS 6 shows a further embodiment of an impeller in a sectional view corresponding to FIGS. 5 and
Fig. 7 Ansicht einer dritten Ausführungsform einesFig. 7 view of a third embodiment of a
Laufrades in Schnittansicht entsprechend Fig. 5 und 6 zusammen mit einem zugehörigen Pum¬ pengehäuse.Impeller in a sectional view corresponding to FIGS. 5 and 6 together with an associated pump housing.
Die in Fig. 1 als ganzes im Längsschnitt dargestellte und mit 1 be¬ zeichnete Kreiselpumpe umfaßt einen Einphasen-Induktionsmotor 2 mit einem außenliegenden Stator 3 und einem innenliegenden drehbar gelagerten Permanentmagnetrotor 4, der axial mit einem Laufrad 5 eines Pumpenteils 6 verbunden und zwischen zwei Lagern, nämlich einem motorseitigen Stecklager 7 und einem pumpenseitigen Stecklager 8 gelagert ist. Letzteres ist in einem Spiralgehäuse 9 des Pumpenteils 6 gehalten, und zwar zentral in einem axialen Einlauf in Form eines Saugkanals 10, durch den die zu pumpende Flüssigkeit, etwa das Wasser eines Springbrunnens mit Hilfe des Laufrades 5 zentrifugal zu einem Auslauf in Form eines Druckstutzens 11 bewegt wird, der mit einer leicht konischen Aufweitung diffusorartig ausge¬ bildet ist, um aus der Strömungsenergie der Flüssigkeit in der Pumpe möglichst verlustarm einen höheren Druck rückzugewinnen.The centrifugal pump shown as a whole in longitudinal section in FIG. 1 and labeled 1 comprises a single-phase induction motor 2 with an external stator 3 and an internal rotatably mounted permanent magnet rotor 4, which is axially connected to an impeller 5 of a pump part 6 and between two bearings , namely a motor-side plug-in bearing 7 and a pump-side plug-in bearing 8. The latter is held in a spiral housing 9 of the pump part 6, specifically centrally in an axial inlet in the form of a suction channel 10, through which the liquid to be pumped, for example the water of a fountain, is centrifuged by means of the impeller 5 to an outlet in the form of a pressure nozzle 11 is moved, which is designed with a slightly conical widening in a diffuser manner, in order to recover a higher pressure from the flow energy of the liquid in the pump with as little loss as possible.
Der Elektromotor 2 der Kreiselpumpe ist ein Einphasen-Synchronmo¬ tor, wobei der Permanentmagnetrotor auf die Überleitung von Strom auf den Rotor und damit auf Bürsten, Schleifringe und KommutatorenThe electric motor 2 of the centrifugal pump is a single-phase synchronous motor, the permanent magnet rotor being used to transfer current to the rotor and thus to brushes, slip rings and commutators
ORIGINAL UNTERLAGEN zu verzichten erlaubt. Damit «vird cas Grundkonzept eines Spaltrohr¬ motors mit einem Spaltrohr 12 möglich, welches den Rotor 4 und das Stecklager 7 wasserdicht umgibt und zum Pumpenteil 6 hin nach außen hin einer ringförmigen Stirnwand in einen äußeren Teil eines Pumpengehäuses übergeht. Denn nur der Stator 3 ist an eine Wech¬ selspannungszufuhr angeschlossen, dabei allerdings von innen und außen durch Spaltrohr 12 und Außengehäuse 13 gekapselt und im übrigen noch in den freibleibenden Bereichen mit Epoxidharz ausge¬ gossen, so daß eine hohe elektrische Sicherheit gewährleistet ist.ORIGINAL DOCUMENTS allowed to do without. Thus "vird cas basic concept of a Spaltrohr¬ motors possible with a split tube 12, which surrounds the rotor 4 and the male bearing 7 waterproof and to the pump portion 6 out to the outside of an annular end wall passes over a pump housing in an outer part. This is because only the stator 3 is connected to an AC voltage supply, but is encapsulated from the inside and outside by the can 12 and the outer housing 13 and is also poured with epoxy resin in the unoccupied areas, so that high electrical safety is ensured.
Ersichtlich ist diese Ausführungsform eines Einphasen-Induktionsmo- tors nicht nur elektrisch überaus sicher, sondern auch im Hinblick auf Kreiselpumpen montagefreundlich, da der Rotor 4 und das Laufrad 5 von der dem Pumpenteil 6 zugewandten offenen Seite des Spalt¬ rohrs 12 eingesteckt werden können, um danach das Spiralgehäuse gleichfalls in axialer Richtung aufzusetzen. Bei bevorzugter Ausfüh¬ rung des Gehäuses in Kunststoff mit der Möglichkeit der Verwendung weitgehend schraubfreier Verbindungen, insbesondere der Möglich¬ keit von Steck- und Rastverbindungen ergibt sich eine äußerst leichte und schnelle Montage.Obviously, this embodiment of a single-phase induction motor is not only extremely safe electrically, but also installation-friendly with regard to centrifugal pumps, since the rotor 4 and the impeller 5 can be inserted from the open side of the can 12 facing the pump part 6 then also place the volute casing in the axial direction. In the preferred embodiment of the housing in plastic with the possibility of using largely screw-free connections, in particular the possibility of plug-in and snap-in connections, this results in extremely easy and quick installation.
Aus Fig. 2 und 3 ist hinsichtlich des Aufbaus des Stators 3 noch näher ersichtlich, daß dieser einen Blechpaket 14 in U-Form mit zwei langgestreckten Schenkeln 15, 16 umfaßt, die jeweils eine Wick¬ lungshälfte 17, 18 der Motorwicklung tragen und endseitig eine im wesentlichen zylindrische Öffnung umgreifen, innerhalb der sich (das nicht dargestellte Spaltrohr 12) und der Rotor 4 befindet. Aus Fig. 3From FIGS. 2 and 3 it can be seen in more detail with regard to the structure of the stator 3 that it comprises a laminated core 14 in a U-shape with two elongated legs 15, 16, each of which carries one winding half 17, 18 of the motor winding and one end encompass substantially cylindrical opening, within which (the can 12, not shown) and the rotor 4 is located. From Fig. 3
ORIGINAL UNTERLAGEN ist erkennbar, daß das Blechpaket 14 den Rotor nicht mit axakt kreis¬ zylindrischen Polschuhflächen umgibt, sondern mit einander gegen¬ überliegenden, allerdings asymmetrisch zum Blechpaket angeordne¬ ten Bereichen 19, 20 einen Magnetspalt schafft, der eine Randlage in bezug auf die Polschuhausformung der Schenkel 15, 16 betont. Dies hat sich in bezug auf den von Haus aus kritischen Anlauf des Ein- phasen-lnduktionsmotors bewährt, da sich der Dauermagnetrotor in Ruhe asymmentrisch ausrichtet und beim Einschalten außerhalb der indifferenten Mittellage liegt. Damit ergibt sich ein generell erleichter¬ ter Anlauf des Rotors.ORIGINAL DOCUMENTS It can be seen that the laminated core 14 does not surround the rotor with axially circular cylindrical pole shoe surfaces, but rather with regions 19, 20 opposite one another, but arranged asymmetrically to the laminated core, creates a magnetic gap which forms an edge position with respect to the pole shoe shape of the legs 15, 16 emphasizes. This has proven itself in relation to the inherently critical start-up of the single-phase induction motor, since the permanent magnet rotor aligns asymmetrically at rest and lies outside of the indifferent central position when switched on. This results in a generally easier starting of the rotor.
Eine bestimmte Drehrichtung des Motors ist in bezug auf eine dreh- richtungsabhängige Ausbildung des Pumpenteils mit richtungsbe- zogener Abstimmung von Laufrad 5 und Spiralgehäuse 9 zwingend erforderlich. Sicherheit in dieser Hinsicht wird gemäß der Erfindung vom Laufrad 5 her geschaffen, welches mit Laufradschaufeln 21 ausgestattet ist, die sich bei einem "falschen" Anlauf des Synchron¬ motors entgegen der vorgegebenen Drehrichtung elastisch auf¬ spreizen. Die herkömmlich bei derartigen Laufrädern nicht erwünschte Verformung kann durch eine allgemeine Elastizität des Werkstoffs und/oder durch eine gezielte Querschnittsgestaltung der Laufradschaufeln insbesondere zu einem mittleren Bereich in der Nähe einer Nabe 22 konstruktiv vorgegeben werden.A certain direction of rotation of the motor is absolutely necessary in relation to a design of the pump part which is dependent on the direction of rotation and with direction-related coordination of the impeller 5 and the spiral housing 9. Safety in this regard is provided according to the invention by the impeller 5, which is equipped with impeller blades 21 which spread out elastically against the specified direction of rotation when the synchronous motor starts up "incorrectly". The deformation which is conventionally not desired in the case of such impellers can be structurally predetermined by a general elasticity of the material and / or by a specific cross-sectional configuration of the impeller blades, in particular with respect to a central region near a hub 22.
Eine Sperre gegen einen "falschen" Anlauf läßt sich grundsätzlich schon dadurch erreichen, daß das beim Rückwärtslauf sich auf¬ spreizende Laufrad einen Strömungswiderstand bildet, bei dem derA lock against a "wrong" start can in principle already be achieved in that the impeller which spreads during reverse running forms a flow resistance in which the
ORIGINAL UNTERLAGEN Einphasen-lndukτions otor süßer Tritt fällt und in eine Pandeibewe- gung übergeht, aus der er dann - gebenenfalls nach weiteren Versu¬ chen - in einen Vorwärts-Anlauf gelangt. Die Laufradschaufeln behal¬ ten dabei in jeder Drehrichtung einen Bewegungsspalt gegenüber dem Pumpengehäuse.ORIGINAL DOCUMENTS Single-phase lnduk τ ions otor sweet passage falls and supply merges into a Pandeibewe- from which it then - optionally after further chen Versu¬ --run forward in a passes. The impeller blades maintain a movement gap with respect to the pump housing in every direction of rotation.
Das Laufrad kann aber auch in bezug auf das Spiralgehäuse 9 so ausgelegt werden, daß die Enden der Laufradschaufeln beim Auf¬ spreizen infolge falscher Laufrichtung mit einer umfangsseitigen In¬ nenwand 23 des Spiralgehäuses oder auch mit nach innen vorsprin¬ genden feststehenden Teilen an diesem, etwa mit rippenartigen oder flossenartigen Anschlägen 24 zusammentreffen. Letzteres ist in Fig. 7 mit einer Darstellung des Laufrads veranschaulicht, bei dem neben der schraffierten Fläche eines Laufrads 25 in gebrochenen Linien auch die aufgespreizte Form des Laufrads 25 bei Rückwärtslauf und die entsprechend gegenüber der Ruhestellung gekrümmte Form der Laufradschaufeln beim Vorwärtslauf eingezeichnet sind.However, the impeller can also be designed with respect to the spiral housing 9 such that the ends of the impeller blades when spreading due to the wrong running direction with a circumferential inner wall 23 of the spiral housing or also with stationary parts projecting inwards thereon, for example meet with rib-like or fin-like stops 24. The latter is illustrated in FIG. 7 with a representation of the impeller, in which, in addition to the hatched area of an impeller 25 in broken lines, the spread shape of the impeller 25 when running in reverse and the shape of the impeller blades correspondingly curved in relation to the rest position are shown during forward running.
Eine Aufspreizung der Laufradschaufeln ab etwa 2 % radialer Länge, d.h. des (radialen) Abstands der Enden der Laufradschaufeln von der zugehörigen Achse kann den Strömungswiderstand im Rückwärtslauf bereits so stark erhöhen, daß der antreibende Einphasen-Indukti- onsmotor keinen Synchronanlauf erreicht. Ebenso kann eine solche begrenzte Aufspreizung genügen, die Laufradschaufeln mit den An¬ schlägen zusammen zu bringen und damit einen "falschen" Anlauf zu stoppen. Vorzugsweise werden die Laufradschaufeln auf eine Auf¬ spreizung von 5 bis 10 % bei Rückwärtslauf ausgelegt.An expansion of the impeller blades from about 2% radial length, i.e. the (radial) distance of the ends of the impeller blades from the associated axis can already increase the flow resistance in reverse so much that the driving single-phase induction motor does not achieve a synchronous start. Such a limited spreading can also suffice to bring the impeller blades together with the stops and thus to stop a "wrong" start-up. The impeller blades are preferably designed for a spread of 5 to 10% when running in reverse.
ORIGINAL UNTERLAGEN 6ORIGINAL DOCUMENTS 6
Eine elastische Ausbildung und/oder Anlenkung der Laufradschaufeln schafft nicht nur drehrichtungsabhängige, sondern auch lastabhän¬ gige Effekte. Während vorbekannte Laufradschaufeln mit starrer Sichelform (bei der fest vorgegebenen Synchrondrehzahl) nur in ei¬ nem sehr begrenzten mittleren Bereich von Förderhöhe und Durch¬ satz gute Leistungen erbringen und einen guten Wirkungsgrad anbie¬ ten, erzielen die erfindungsgemäß nachgiebig gestalteten Laufrad¬ schaufeln über Förderhöhe und Durchsatz weite Arbeitsbereiche mit guter Leistung und hohem Wirkungsgrad. Überdies ist die vom Syn¬ chronmotor angeforderte und aufzubringende Leistung - anders als bei herkömmlichen Pumpen - über den gesamten Bereich, d.h. in dem Grenzbereich mit maximaler Förderhöhe (Durchsatz 0) ebenso wie im Grenzbereich mit maximalem Durchsatz (Förderhöhe 0) wie in mittleren Arbeitsbereichen etwa konstant und paßt sich damit der Leistungskennlinie des Synchronmotors vorzüglich an. Dies führt insgesamt zu einer sehr guten Leistungsausbeute im Rahmen der gegebenen Baugröße.An elastic design and / or articulation of the impeller blades creates not only effects dependent on the direction of rotation, but also load-dependent effects. While known impeller blades with a rigid sickle shape (at the fixed, predetermined synchronous speed) only perform well and offer good efficiency in a very limited middle range of head and throughput, the impeller blades, which are designed according to the invention, achieve over head and Throughput wide work areas with good performance and high efficiency. Moreover, unlike conventional pumps, the power requested and to be applied by the synchronous motor is over the entire range, i.e. in the border area with maximum delivery head (throughput 0) as well as in the border area with maximum throughput (delivery head 0) as in middle working areas approximately constant and thus adapts perfectly to the performance characteristic of the synchronous motor. Overall, this leads to a very good performance yield within the given size.
Daneben ergibt sich über den gesamten Leistungsbereich der Mo¬ torpumpe eine besondere Laufruhe. Gerade durch die durchgängig hohe, von der Pumpenbelastung nach Förderhöhe und Durchsatz wenig abhängige Motorbelastung läßt sich ein Vollast-Betrieb sicher¬ stellen. Damit wird ein Teillastbetrieb vermieden, in dem gerade Ein- phasen-Synchronmotoren zu starken Schwingungen mit nach außen dringenden Vibrationen und Geräuschen neigen. Diese EigenschaftenIn addition, there is a particularly smooth running over the entire performance range of the motor pump. Full load operation can be ensured precisely through the consistently high motor load, which is not dependent on the pump load according to the head and throughput. This avoids partial load operation, in which single-phase synchronous motors in particular tend to vibrate strongly with vibrations and noises escaping to the outside. These properties
ORIGINAL UNTERLAGEN sind gerade bei k'einen und einfachen Motorpumpen der hier infrage stehenden Art herausragend.ORIGINAL DOCUMENTS are outstanding especially with no and simple motor pumps of the type in question here.
Für den Fall, daß die elastische Ausbildung der Laufradschaufeln für ein Aufspreizen beim Rückwärtslauf zu einer unerwünscht starken Verformung beim Vorwärtslauf führt, können die Schaufeln durch Di¬ stanzstützen stabilisiert werden. In Fig. 5 sind Distanzstützen 26 ver¬ anschaulicht, die von der Nabe 22 ausgehend schwertartig in einer mittleren Radialebene verlaufen und damit die Strömung im Pumpen¬ teil wenig beeinflußen, die Schaufeln abstützen, wenn sie sich unter Last zurückbiegen.In the event that the elastic configuration of the impeller blades for spreading apart during reverse running leads to an undesirably strong deformation during forward running, the blades can be stabilized by distance supports. 5 shows spacer supports 26 which, starting from the hub 22, run in a sword-like manner in a central radial plane and thus have little influence on the flow in the pump part and support the blades when they bend back under load.
Eine ganz ähnliche Wirkung läßt sich mit Distanzstützen 27 bei einem Laufrad 28 gemäß Fig. 6 erzielen, die nicht an einer Laufradnabe 29, sondern als rückwärtige Flossen an Laufradschaufeln 30 ansetzen.A very similar effect can be achieved with spacer supports 27 on an impeller 28 according to FIG. 6, which do not attach to an impeller hub 29 but to the impeller blades 30 as rear fins.
Wie insbesondere die Fig. 1 , 2 und 4 verdeutlichen, kann die Momen¬ tenübertragung zwischen Rotor 4 und Laufrad 5 mit Hilfe einer Freilaufkupplung erfolgen, bei der eine koaxiale Zuordnung einer Steckwelle 31 und einer Mitnehmerhülse 32 rastend zusammenge¬ bracht werden, wobei die Mitnehmerhülse 32 soweit frei gegenüber der Welle 31 über einen Winkelbereich, hier von mehr als 120° zu beiden Seiten verdrehbar ist, bis eine Mitnehmernase 33 an der Hülse 32 auf der einen oder anderen Seite gegen einen Mitnehmer¬ anschlag 34 trifft, der mit der Welle 31 umläuft. Der damit geschaffene Freilauf kann in vielen Fällen nützlich sein, den heiklen Anlauf des Einphasen-Induktionsmotors zu erleichtern, da dieser nicht unter Last1, 2 and 4 in particular, the torque transmission between rotor 4 and impeller 5 can take place with the aid of a one-way clutch, in which a coaxial assignment of a stub shaft 31 and a driving sleeve 32 are brought together in a latching manner, the driving sleeve 32 as far as is freely rotatable relative to the shaft 31 over an angular range, here of more than 120 ° on both sides, until a driver lug 33 on the sleeve 32 on one side or the other meets a driver stop 34 which is connected to the shaft 31 circulates. The freewheel created in this way can be useful in many cases to facilitate the delicate start of the single-phase induction motor, since it is not under load
ORIGINAL UNTERLAGEN 1 0 erfolgt. Es hat sich allerdings g zeigt, daß durch eine geεigr.εt3 Aus¬ legung des Laufrades mit der feder-elastischen Ausbildung der Laufradschaufeln ein Anlauf - in Vorwärtsrichtung - gefördert wird, der vielfach auf einen solchen Freilauf zu verzichten ermöglicht. Letzteres ist insbesondere bei Massenprodukten unter Verwendung möglicht weniger Teile, insbesondere spritzgegossener Teile aus Kunststoff, und bei einem Zwang zur einfachen Montage und kurzen Montage¬ zeiten ein wesentlicher Fertigungsvorteil.ORIGINAL DOCUMENTS 1 0 is done. However, it has been shown that a start-up - in the forward direction - is promoted by a geεigr.εt3 design of the impeller with the spring-elastic design of the impeller blades, which often makes it possible to dispense with such a freewheel. The latter is in particular in the case of mass products using as few parts as possible, in particular injection-molded parts made of plastic, and in the case of a requirement for simple assembly and short assembly times, an essential manufacturing advantage.
ORIGINAL UNTERLAGEN ORIGINAL DOCUMENTS

Claims

1. Kreiselpumpe, insbesondere für Springbrunnen und Aquarien, bei der ein Elektromotor und eine Pumpe koaxial zueinander ange¬ ordnet sind, wobei der Elektromotor als Einphasen-Synchronmotor mit einem Permanentmagnetrotor ausgebildet und mit einem offenen Laufrad der Pumpe mit von einer Nabe nach außen spiralförmig bezüglich einer vorgegebenen Drehrichtung zurückgebogenen Laufradschaufeln verbunden ist, dadurch gekennzeichnet, daß die Laufradschaufeln (21, 30) derart elastisch ausgebildet sind, daß sie sich bei einem Anlauf des Synchronmotors (2) entgegen der vorge¬ gebenen Drehrichtung um zumindest 2 % in radialer Länge auf¬ spreizen.1. Centrifugal pump, in particular for fountains and aquariums, in which an electric motor and a pump are arranged coaxially with one another, the electric motor being designed as a single-phase synchronous motor with a permanent magnet rotor and with an open impeller of the pump with a spiral from one hub to the outside Impeller blades bent back in a predetermined direction of rotation, characterized in that the impeller blades (21, 30) are designed to be elastic in such a way that when the synchronous motor (2) starts up, at least 2% in radial length counter to the specified direction of rotation spread.
2. Kreiselpumpe nach Anspruch 1 , dadurch gekennzeichnet, daß die Laufradschaufeln (21, 30) in aufgespreiztem Zustand in einem zumindest einen Bewegungsspalt belassenden Abstand vom Pum¬ pengehäuse (9) enden.2. Centrifugal pump according to claim 1, characterized in that the impeller blades (21, 30) in the expanded state in an at least one movement gap leaving distance from the pump housing (9) end.
ORIGINAL UNTERLAGEN 1 2ORIGINAL DOCUMENTS 1 2
3. Kreiselpumpe n-*ch Ansnruch 1 , dadurch gekennzeichnet, daß die aufgestellten Laufradschaufeln (21 , 30) die in radialer Richtung angeordnete Innenwand (23) des Pumpengehäuses berühren.3. Centrifugal pump n- * ch Ansnruch 1, characterized in that the impeller blades (21, 30) touch the radially arranged inner wall (23) of the pump housing.
4. Kreiselpumpe nach Anspruch 3, dadurch gekennzeichnet, daß die Innenwand (23) mit zumindest einem Anschlag (24) für die sich aufstellenden Laufradschaufeln (21 , 30) versehen ist.4. Centrifugal pump according to claim 3, characterized in that the inner wall (23) is provided with at least one stop (24) for the impeller blades (21, 30).
5. Kreiselpumpe nach einem der Ansprüche 2 bis 4, dadurch ge¬ kennzeichnet, daß das Laufrad (5, 28) zwischen den Laufradschau¬ feln Distanzstützen (26, 27) aufweist.5. Centrifugal pump according to one of claims 2 to 4, characterized ge indicates that the impeller (5, 28) has spacer supports (26, 27) between the impeller blades.
6. Kreiselpumpe nach Anspruch 5, dadurch gekennzeichnet, daß die Distanzstützen (26, 27) schwertförmig mit einer den Laufrad¬ schaufeln angepaßten Kontur ausgebildet sind.6. Centrifugal pump according to claim 5, characterized in that the spacer supports (26, 27) are sword-shaped with a contour adapted to the impeller blades.
7. Kreiselpumpe nach Anspruch 5 oder 6, dadurch gekennzeich¬ net, daß die Distanzstützen (26) von der Nabe (22) des Laufrades (5) aus vorwiegend radial nach außen verlaufen.7. Centrifugal pump according to claim 5 or 6, characterized gekennzeich¬ net that the spacer supports (26) from the hub (22) of the impeller (5) extend predominantly radially outwards.
8. Kreiselpumpe nach Anspruch 5, dadurch gekennzeichnet, daß die Distanzstützen (27) an den Laufradschaufeln (30) angeordnet sind und sich von diesen in Umlaufrichtung nachlaufend erstrecken.8. Centrifugal pump according to claim 5, characterized in that the spacers (27) are arranged on the impeller blades (30) and extend from them in the circumferential direction.
9. Kreiselpumpe nach Anspruch 8, dadurch gekennzeichnet, daß die Distanzstützen (26, 27) flächig ausgebildet sind und in einer Bewegungsebene des Laufrads liegen.9. Centrifugal pump according to claim 8, characterized in that the spacers (26, 27) are flat and lie in a plane of movement of the impeller.
ORIGINAL UNTERLAGEN PC17EP95/02770ORIGINAL DOCUMENTS PC17EP95 / 02770
1 31 3
10. Kreiselpumpe nach einem der Ansprüche 1 bis 9, gekennzeich¬ net durch eine einen winkelbegrenzten Freilauf gewährende Freilauf¬ kupplung (31, 32, 33, 34) zwischen Laufrad (5) und Rotor (4).10. Centrifugal pump according to one of claims 1 to 9, gekennzeich¬ net by an angularly limited freewheeling freewheel clutch (31, 32, 33, 34) between the impeller (5) and rotor (4).
11. Kreiselpumpe nach Anspruch 10, dadurch gekennzeichnet, daß der Freilauf mehr als 120° zu beiden Seiten beträgt.11. Centrifugal pump according to claim 10, characterized in that the freewheel is more than 120 ° on both sides.
12. Kreiselpumpe nach einem der Ansprüche 1 bis 11 , dadurch ge¬ kennzeichnet, daß das Pumpengehäuse als Spiralgehäuse (9) aus¬ gebildet ist.12. Centrifugal pump according to one of claims 1 to 11, characterized in that the pump housing is formed as a spiral housing (9).
13. Kreiselpumpe nach einem der Ansprüche 1 bis 12, dadurch gekennzeichnet, daß ein Spaltrohr (12) den Rotor (4) und den Sta¬ tor (3) des Einphasen-Synchronmotors voneinander trennt, wobei der Rotor (4) zusammen mit der Pumpe (6) in einem gemeinsamen Naßbereich liegt.13. Centrifugal pump according to one of claims 1 to 12, characterized in that a can (12) separates the rotor (4) and the gate (3) of the single-phase synchronous motor, the rotor (4) together with the pump (6) is in a common wet area.
ORIGINAL UNTERLAGEN ORIGINAL DOCUMENTS
EP95926885A 1994-07-15 1995-07-14 Centrifugal pump, especially for fountains Expired - Lifetime EP0723631B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE4424996 1994-07-15
DE4424996A DE4424996A1 (en) 1994-07-15 1994-07-15 Centrifugal pump, especially for fountains
PCT/EP1995/002770 WO1996002763A1 (en) 1994-07-15 1995-07-14 Centrifugal pump, especially for fountains

Publications (2)

Publication Number Publication Date
EP0723631A1 true EP0723631A1 (en) 1996-07-31
EP0723631B1 EP0723631B1 (en) 1998-08-05

Family

ID=6523229

Family Applications (1)

Application Number Title Priority Date Filing Date
EP95926885A Expired - Lifetime EP0723631B1 (en) 1994-07-15 1995-07-14 Centrifugal pump, especially for fountains

Country Status (7)

Country Link
US (1) US5711657A (en)
EP (1) EP0723631B1 (en)
AT (1) ATE169379T1 (en)
DE (2) DE4424996A1 (en)
DK (1) DK0723631T3 (en)
ES (1) ES2122663T3 (en)
WO (1) WO1996002763A1 (en)

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Also Published As

Publication number Publication date
DE59503069D1 (en) 1998-09-10
EP0723631B1 (en) 1998-08-05
ES2122663T3 (en) 1998-12-16
DE4424996A1 (en) 1996-01-18
US5711657A (en) 1998-01-27
WO1996002763A1 (en) 1996-02-01
ATE169379T1 (en) 1998-08-15
DK0723631T3 (en) 1999-05-03

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