EP3004649B1 - Pump arrangement - Google Patents

Pump arrangement Download PDF

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Publication number
EP3004649B1
EP3004649B1 EP14726122.6A EP14726122A EP3004649B1 EP 3004649 B1 EP3004649 B1 EP 3004649B1 EP 14726122 A EP14726122 A EP 14726122A EP 3004649 B1 EP3004649 B1 EP 3004649B1
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EP
European Patent Office
Prior art keywords
pump
pump arrangement
arrangement according
impeller
inner rotor
Prior art date
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Application number
EP14726122.6A
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German (de)
French (fr)
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EP3004649A1 (en
Inventor
Patrick Drechsel
Markus Lay
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KSB SE and Co KGaA
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KSB SE and Co KGaA
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Publication of EP3004649A1 publication Critical patent/EP3004649A1/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
    • F04D25/00—Pumping installations or systems
    • F04D25/02—Units comprising pumps and their driving means
    • F04D25/06—Units comprising pumps and their driving means the pump being electrically driven
    • 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
    • F04D13/024—Units comprising pumps and their driving means containing a coupling a magnetic coupling
    • F04D13/025—Details of the can separating the pump and drive area
    • 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
    • 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
    • F04D13/024—Units comprising pumps and their driving means containing a coupling a magnetic 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
    • 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
    • F04D13/024—Units comprising pumps and their driving means containing a coupling a magnetic coupling
    • F04D13/026—Details of the bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D17/08—Centrifugal pumps
    • F04D17/10—Centrifugal pumps for compressing or evacuating
    • 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
    • F04D29/60—Mounting; Assembling; Disassembling
    • F04D29/62—Mounting; Assembling; Disassembling of radial or helico-centrifugal pumps
    • F04D29/628—Mounting; Assembling; Disassembling of radial or helico-centrifugal pumps especially adapted for liquid pumps

Definitions

  • the invention relates to a modular kit for designing sizes for a hydraulic size with different magnetic coupling sizes or for a magnetic coupling size and different hydraulic sizes for producing a pump arrangement according to the preamble of claim 1.
  • the invention also relates to such a pump arrangement.
  • Such a pump assembly is from DE 10 2004 003 400 A1 known, which has a drive rotor to increase the area of application, which is designed as a common part for external drive elements.
  • the DE 43 43 854 A1 discloses a magnetic pump for corrosive media, wherein the pump shaft consists of hard ceramic and the impeller bushing with the impeller and the magnet rotor bushing with the magnet rotor are cast in a torque-proof manner and the pump shaft is non-rotatably connected to the impeller bushing and the magnet rotor bushing via a polygonal profile.
  • a magnetic drive pump with permanent magnets made of certain materials is from the GB 994 322 A famous.
  • the US 4,871,301A discloses a magnetic drive pump with a bearing system that includes a lubrication system that uses the pumped medium as a lubricant and coolant in some cases.
  • a pump which has an axially adjustable impeller in order to adjust the distance between the impeller and the housing.
  • the pump has a removable module that includes the impeller, the impeller shaft, and a drive member.
  • the object of the invention is to provide a magnetic coupling pump arrangement in which the largest possible number of magnetic couplings with different diameters are available for one hydraulic size and as many different hydraulic sizes as possible can be used for one magnetic coupling size.
  • different containment shells ie different pressure levels and/or materials, should be usable within one magnetic coupling size.
  • the object of the invention is achieved by various adapter elements which connect the containment shell to the housing cover and have a mounting flange which rests against a contact surface of the housing cover on the side close to the interior.
  • a modular construction kit is available, which enables an efficient size design for a hydraulic size with different magnetic coupling sizes or for a magnetic coupling size and different hydraulic sizes.
  • a magnetic coupling size can be adapted to different hydraulic sizes by adapting the shape and/or size of the adapter element. This covers the large range of torques required for one and the same hydraulic size due to different speeds, delivery heights, delivery volumes and densities of the medium to be delivered. It is no longer necessary to use the maximum coupling size for all combinations, but the appropriate magnetic coupling size can be adapted to a hydraulic size, with corresponding advantages in terms of energy efficiency, eddy current losses and/or procurement costs. Another advantage of the invention is the reduced number of components to be stocked for a pump series.
  • the contact surface has a region which is set back in the axial direction and into which a centering ring formed on the mounting flange engages.
  • a sealing ring can be arranged in the recessed area and, on the other hand, the adapter element can be precisely aligned and fastened to the housing cover in a fluid-tight manner.
  • the adapter element has several threaded holes for fastening the containment shell on the side opposite the mounting flange, it is possible to use or exchange different containment shells of different pressure levels or strengths and/or different materials within one magnetic coupling size.
  • a ring which extends further into the interior in the axial direction and which forms a start-up safeguard and prevents the outer rotor from touching the containment shell.
  • the outer contour of the adapter element has an essentially conical shape.
  • the adapter element preferably tapers essentially starting from the mounting flange up to the ring.
  • the end of the outer rotor pointing in the direction of the housing cover has a radially circumferential projection.
  • the projection is formed on the inside of the ring.
  • the end of the outer rotor pointing in the direction of the housing cover has a region with a reduced outer diameter. This ensures that the adapter element can be assembled with small coupling diameters.
  • a bearing arrangement which is in operative connection with the impeller shaft which can be driven in rotation about the axis of rotation is arranged between the impeller and the inner rotor.
  • a spring device is arranged between the inner rotor and the bearing arrangement.
  • the spring device in one embodiment between the spring device and the inner rotor there is a spacer sleeve pushed onto the impeller shaft, by means of which the inner rotor gets deeper into the outer rotor in the axial direction.
  • the magnets of the inner rotor and the magnets of the outer rotor are thus optimally aligned with one another in order to ensure optimum power transmission from the outer rotor to the inner rotor.
  • the object of the invention is also achieved by a modular kit for producing a pump arrangement according to the invention.
  • the 1 shows a pump arrangement 1 in the form of a magnetic coupling pump arrangement.
  • the pump arrangement 1 has a multi-part pump housing 2 of a centrifugal pump, which includes a hydraulic housing 3 designed as a volute housing, a housing cover 4 , a bearing bracket lantern 5 , a bearing bracket 6 and a bearing cover 7 .
  • the hydraulic housing 3 has an inlet opening 8 for sucking in a pumped medium and an outlet opening 9 for ejecting the pumped medium.
  • the housing cover 4 is arranged on the side of the hydraulic housing 3 opposite the inlet opening 8 .
  • the bearing bracket lantern 5 is attached to the side of the housing cover 4 facing away from the hydraulic housing 3 .
  • the bearing carrier 6 is attached to the side of the bearing carrier lantern 5 opposite the housing cover 4 .
  • the bearing cap 7 is in turn fastened to the side of the bearing carrier 6 facing away from the bearing carrier lantern 5 .
  • a containment shell 10 is attached to the side of the housing cover 4 facing away from the hydraulic housing 3 and extends at least partially through an interior space 11 delimited by the pump housing 2, in particular by the housing cover 4, by the bearing bracket lantern 5 and by the bearing bracket 6.
  • the containment shell 10 has an im Substantially cylindrical body 12 on.
  • the base body 12 is open on one side and closed on the side opposite the open side by means of a curved bottom 13 .
  • a ring-like fastening flange 14 which is formed in one piece with the base body 12 or is connected thereto by welding or by means of other suitable fastening means or devices, for example screws, rivets or the like.
  • the mounting flange 14 rests on the side close to the interior 11 against a contact surface 15 of the housing cover 4 and has a plurality of mounting holes 16 through which screws 17 can be passed and screwed into threaded holes 18 provided in the housing cover 4 .
  • the containment shell 10 hermetically seals a chamber 19 enclosed by it and the housing cover 4 from the interior 11 .
  • An impeller shaft 20 rotatable about an axis of rotation A extends from a flow chamber 21 delimited by the hydraulic housing 3 and the housing cover 4 through an opening 22 provided in the housing cover 4 into the chamber 19
  • Impeller 23 attached, at the opposite end of the shaft, which has two shaft sections 20a, 20b, each with increasing diameters, an inner rotor 24 arranged within the chamber 19 is provided.
  • the inner rotor 24 is fitted with a plurality of magnets 25 which are arranged on the side of the inner rotor 24 which faces the can 10 .
  • a bearing arrangement 26 Arranged between the impeller 23 and the inner rotor 24 is a bearing arrangement 26 which is operatively connected to the impeller shaft 20 which can be driven so as to rotate about the axis of rotation A.
  • a bearing ring carrier 27 arranged coaxially to the axis of rotation A, with which the stationary parts of the bearing arrangement 26, i.e. those parts that do not rotate with the impeller shaft 20, are held in place, has a flange-like area 28 on another contact surface 29 of the housing cover 4 attached to the housing cover 4 by means of a screw connection (not shown) and extends into the chamber 19.
  • a spring device 30 in the form of a plate spring assembly is arranged between the inner rotor 24 or the shaft section 20a and the bearing arrangement 26, in particular the parts of the bearing arrangement 26 rotating with the impeller shaft 20, and acts on the clamping assembly, consisting of impeller 23, one impeller 23 impeller nut 32 fastened to the impeller shaft 20 via a disc 31, the parts of the bearing arrangement 26 rotating with the impeller shaft 20 and the inner rotor 24 with a spring force such that the clamping connection, in particular via the inner rotor 24, is held to a certain extent elastically in contact with a contact surface 33, which arises from the different diameters of the shaft sections 20a and 20b, the diameter of the shaft section 20b being larger than the diameter of the shaft section 20a.
  • the clamping assembly thus essentially comprises the components rotating about the axis of rotation A with the impeller shaft 20 .
  • a drive motor not shown, preferably an electric motor, drives a drive shaft 34 .
  • the drive shaft 34 which can be driven about the axis of rotation A, is arranged essentially coaxially with the impeller shaft 20 .
  • the drive shaft 34 extends through the bearing cover 7, the bearing bracket 6 and at least partially into the bearing bracket lantern 5.
  • the drive shaft 34 is mounted in two ball bearings 35, 36 accommodated in the bearing bracket 6.
  • the magnets 37 are arranged on the side of the outer rotor 38 facing the can 10 .
  • the outer rotor 38 extends at least partially over the containment shell 10 and interacts with the inner rotor 24 in such a way that the rotating outer rotor 38 also causes the inner rotor 24 and thus the impeller shaft 20 and the impeller 23 to rotate by means of magnetic forces.
  • the 2 shows a pump assembly 1, whose external dimensions in the 1 correspond to the external dimensions shown.
  • the hydraulic housing 3, the housing cover 4, the bearing bracket lantern 5, the bearing bracket 6 and the bearing cap 7 have the same dimensions.
  • impeller 23, bearing arrangement 26 and bearing ring carrier 27 have the same dimensions in both embodiments.
  • the inner rotor 24 and the outer rotor 38 are smaller than in the case of FIG 1 embodiment shown. This is particularly advantageous when the pump arrangement 1 has lower performance requirements, for example a lower delivery height or delivery quantity, with the highest possible efficiency.
  • a separate adapter element 39 is provided for adapting the containment shell 10 with a reduced axial extension and a reduced diameter, on one side has a mounting flange 40, the configuration of which is substantially the same as that in the 1 shown mounting flange 14 of the containment shell 10 corresponds.
  • the mounting flange 40 rests against the contact surface 15 of the housing cover 4 on the side close to the interior 11 and has a plurality of mounting holes 41 through which the screws 17 can be passed and screwed into the threaded holes 18 provided in the housing cover 4 .
  • the contact surface 15 has a region 42 set back in the axial direction, in which a sealing ring 43 is arranged and in which a centering ring 44 formed on the mounting flange 40 engages, as a result of which the adapter element 39 can be precisely aligned and fastened to the housing cover 4 in a fluid-tight manner.
  • the adapter element 39 On the side opposite the mounting flange 40, the adapter element 39 has a plurality of threaded holes 45 into which screws 46 extending through the mounting holes 16 in the mounting flange 14 of the containment shell 10 can be screwed. This makes it possible to exchange different containment shells 10 of different pressure stages or strengths and/or different materials within one magnetic coupling size.
  • a ring 47 which extends further into the interior 11 in the axial direction and which forms a safety device and prevents the magnets 37 of the outer rotor 38 from touching the base body 12 of the containment shell 10 .
  • the outer contour of the adapter element 39 each have an essentially conical shape.
  • the adapter element 39 tapers down to the ring 47.
  • the inner contour of the adapter element 39 is at least partially tapered.
  • the end of the outer rotor 38 pointing in the direction of the housing cover 4 has a radially circumferential projection 48 facing the ring 47, which in any case first touches the inside of the ring 47 of the adapter element 39 if the outer rotor 38 is possibly rotating with an imbalance before the Magnets 37 of the outer rotor 38 come into contact with the base body 12 of the containment shell 10 .
  • the projection 48 can also be formed on the inside of the ring 47 .
  • the projection 48 can be formed both at the end of the outer rotor 38 and on the inside of the ring 47.
  • the impeller shaft 20 is by the length of the spacer sleeve 49 compared to that in FIG 1 embodiment shown extended.
  • the inner rotor 24 moves deeper into the outer rotor 38 in the axial direction by means of the spacer sleeve 49.
  • the magnets 25 of the inner rotor 24 and the magnets 37 of the outer rotor 38 are thus optimally aligned with one another in order to ensure optimal power transmission from the outer rotor 38 to the inner rotor 24.
  • the 3 shows a pump assembly 1, whose external dimensions in the 1 and 2 correspond to the external dimensions shown.
  • impeller 23, bearing assembly 26 and bearing ring carrier 27 have the same dimensions as in the 1 and 2 embodiments shown on.
  • the embodiment shown are both the diameter and the axial extent of containment shell 10, inner rotor 24 and outer rotor 38 compared to that in FIG 2 embodiment shown has been further reduced.
  • the impeller shaft 20, in particular shaft section 20a, has the same axial extent as in the case of FIG 2 embodiment shown.
  • the end of the outer rotor 38 pointing in the direction of the housing cover 4 has an area 50 facing the ring 47 with a reduced outer diameter, with which an outer rotor 38 possibly rotating with an imbalance first comes into contact with the inside of the ring 47 of the adapter element 39 , before the magnets 37 of the outer rotor 38 come into contact with the base body 12 of the can 10.
  • the adapter element 39 can also be used on a housing cover 4 designed as a heat barrier in a pump arrangement 1 carrying a hot medium.
  • the hydraulic housing 3, major areas of the housing cover 4, bearing bracket lantern 5, bearing bracket 6 and bearing cap 7 have the same dimensions as in the Figures 1 to 3 shown embodiments on.
  • the containment shell 10, the adapter element 39 and the outer rotor 38 have the same dimensions according to the size of the magnetic coupling 2 on.

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Description

Die Erfindung betrifft einen modularen Baukasten zur Baugrößenauslegung für eine Hydraulikgröße mit unterschiedlichen Magnetkupplungsgrößen bzw. für eine Magnetkupplungsgröße und verschiedenen Hydraulikgrößen zur Herstellung einer Pumpenanordnung nach dem Oberbegriff des Anspruchs 1. Die Erfindung betrifft ferner eine derartige Pumpenanordnung.The invention relates to a modular kit for designing sizes for a hydraulic size with different magnetic coupling sizes or for a magnetic coupling size and different hydraulic sizes for producing a pump arrangement according to the preamble of claim 1. The invention also relates to such a pump arrangement.

Eine derartige Pumpenanordnung ist aus der DE 10 2004 003 400 A1 bekannt, die zum Vergrößern des Anwendungsbereiches einen Antriebsrotor aufweist, der als ein Gleichteil für äußere Antriebselemente ausgebildet ist. Dadurch ist aber eine Vergrößerung des Anwendungsbereiches nur bis zu einem bestimmten Grad möglich. Ab einer gewissen Baugröße ist eine Anpassung der Rotorgröße unvermeidlich.Such a pump assembly is from DE 10 2004 003 400 A1 known, which has a drive rotor to increase the area of application, which is designed as a common part for external drive elements. However, this means that the area of application can only be increased to a certain extent. From a certain size, an adjustment of the rotor size is unavoidable.

Aus der EP 0 814 268 A1 ist ein modularer Bausatz zur Herstellung von Pumpen bekannt, der die Möglichkeiten bieten soll, Pumpen nach Anwendungsbedarf beliebig aus wenigen Bauelementen zu produzieren. Die vorgeschlagene Lösung lässt jedoch nur den Austausch von Bauteilen zu, die einer einzigen Baugröße zugeordnet sind.From the EP 0 814 268 A1 a modular kit for the production of pumps is known, which should offer the possibility of producing pumps from a few components according to application requirements. However, the proposed solution only allows the replacement of components that are associated with a single size.

Die DE 43 43 854 A1 offenbart eine Magnetpumpe für korrosive Medien, wobei die Pumpenwelle aus Hartkeramik besteht und die Laufradbuchse mit dem Laufrad und die Magnetrotorbuchse mit dem Magnetrotor drehfest vergossen sind und die Pumpenwelle über je ein Polygonprofil formschlüssig mit der Laufradbuchse und der Magnetrotorbuchse drehfest verbunden ist.the DE 43 43 854 A1 discloses a magnetic pump for corrosive media, wherein the pump shaft consists of hard ceramic and the impeller bushing with the impeller and the magnet rotor bushing with the magnet rotor are cast in a torque-proof manner and the pump shaft is non-rotatably connected to the impeller bushing and the magnet rotor bushing via a polygonal profile.

Eine Magnetkupplungspumpe, bei der die Pumpenwelle in den Gleitlagern axial verschiebbar gelagert ist, und das Laufrad drehfest mit der Pumpenwelle verbunden und auf dieser axial verschiebbar angeordnet ist, wird in der DE 297 16 110 U1 gezeigt.In the DE 297 16 110 U1 shown.

Eine Magnetkupplungspumpe mit Permanentmagneten aus bestimmten Materialien ist aus der GB 994 322 A bekannt.A magnetic drive pump with permanent magnets made of certain materials is from the GB 994 322 A famous.

Die US 4,871,301 A offenbart eine Magnetkupplungspumpe mit einem Lagersystem, das ein Schmiersystem umfasst, das in manchen Fällen das geförderte Medium als Schmier- und Kühlmittel benutzt.the US 4,871,301A discloses a magnetic drive pump with a bearing system that includes a lubrication system that uses the pumped medium as a lubricant and coolant in some cases.

Aus der US 5,846,049 A ist eine Pumpe bekannt, die ein axial einstellbares Laufrad aufweist, um den Abstand zwischen Laufrad und Gehäuse einzustellen. Die Pumpe hat ein ausbaubares Modul, das das Laufrad, die Laufradwelle und ein Antriebselement umfasst.From the US 5,846,049A a pump is known which has an axially adjustable impeller in order to adjust the distance between the impeller and the housing. The pump has a removable module that includes the impeller, the impeller shaft, and a drive member.

Das Dokument " Johnson Pump - Combi Modular System", veröffentlicht im Februar 2008 , offenbart ein modulares System für einstufige Kreiselpumpen mit zwischen den unterschiedlichen Pumpenkonstruktionen austauschbaren Teilen.The document " Johnson Pump - Combi Modular System", published February 2008 , discloses a modular system for single stage centrifugal pumps with interchangeable parts between the different pump designs.

Die vorstehend genannten Schriften berücksichtigen jedoch nicht, dass, bedingt durch verschiedene Drehzahlen, Förderhöhen, Fördervolumina und Dichten des zu fördernden Mediums, für ein und dieselbe Hydraulikgröße ein großer Bereich an Drehmomenten benötigt wird.However, the documents mentioned above do not take into account that, due to different speeds, delivery heights, delivery volumes and densities of the medium to be delivered, a large range of torques is required for one and the same hydraulic size.

Die Aufgabe der Erfindung besteht darin, eine Magnetkupplungspumpenanordnung bereitzustellen, bei der für eine Hydraulikgröße eine möglichst große Zahl von Magnetkupplungen mit unterschiedlichen Durchmessern zur Verfügung steht und für eine Magnetkupplungsgröße möglichst viele unterschiedliche Hydraulikgrößen verwendbar sind. Gleichsam sollten innerhalb einer Magnetkupplungsgröße unterschiedliche Spalttöpfe, d.h. unterschiedliche Druckstufen und/oder Werkstoffe, verwendbar sein.The object of the invention is to provide a magnetic coupling pump arrangement in which the largest possible number of magnetic couplings with different diameters are available for one hydraulic size and as many different hydraulic sizes as possible can be used for one magnetic coupling size. At the same time, different containment shells, ie different pressure levels and/or materials, should be usable within one magnetic coupling size.

Die Aufgabe der Erfindung wird gelöst durch verschiedene den Spalttopf mit dem Gehäusedeckel, verbindende Adapterelemente mit einem Montageflansch, der an der dem Innenraum nahen Seite an einer Anlagefläche des Gehäusedeckels, anliegt.The object of the invention is achieved by various adapter elements which connect the containment shell to the housing cover and have a mounting flange which rests against a contact surface of the housing cover on the side close to the interior.

Durch die Verwendung verschiedener Adapterelemente steht ein modularer Baukasten zur Verfügung, der eine effiziente Baugrößenauslegung für eine Hydraulikgröße mit unterschiedlichen Magnetkupplungsgrößen bzw. für eine Magnetkupplungsgröße und verschiedenen Hydraulikgrößen ermöglicht.By using different adapter elements, a modular construction kit is available, which enables an efficient size design for a hydraulic size with different magnetic coupling sizes or for a magnetic coupling size and different hydraulic sizes.

In einfacher Art und Weise lässt sich also durch form- und/oder größenmäßige Anpassung des Adapterelementes eine Magnetkupplungsgröße an verschiedene Hydraulikgrößen adaptieren. Dadurch wird der für ein und dieselbe Hydraulikgröße durch verschiedene Drehzahlen, Förderhöhen, Fördervolumina und Dichten des zu fördernden Mediums bedingte große erforderliche Bereich an Drehmomenten abgedeckt. Es braucht nicht mehr die jeweils maximale Kupplungsgröße für alle Kombinationen verwendet zu werden, sondern es kann jeweils die passende Magnetkupplungsgröße an eine Hydraulikgröße adaptiert werden, mit entsprechenden Vorteilen hinsichtlich der Energieeffizienz, der Wirbelstromverluste und/oder der Anschaffungskosten. Ein weiterer Vorteil der Erfindung ist die verringerte Anzahl der zu bevorratenden Bauteile für eine Pumpenbaureihe.In a simple way, a magnetic coupling size can be adapted to different hydraulic sizes by adapting the shape and/or size of the adapter element. This covers the large range of torques required for one and the same hydraulic size due to different speeds, delivery heights, delivery volumes and densities of the medium to be delivered. It is no longer necessary to use the maximum coupling size for all combinations, but the appropriate magnetic coupling size can be adapted to a hydraulic size, with corresponding advantages in terms of energy efficiency, eddy current losses and/or procurement costs. Another advantage of the invention is the reduced number of components to be stocked for a pump series.

In weiterer Ausgestaltung weist die Anlagefläche einen in axialer Richtung zurückgesetzten Bereich auf, in den ein an dem Montageflansch ausgebildeter Zentrierring eingreift. In dem zurückgesetzten Bereich ist zum Einen ein Dichtungsring anordenbar und zum Anderen ist das Adapterelement exakt ausrichtbar und fluiddicht an dem Gehäusedeckel befestigbar.In a further embodiment, the contact surface has a region which is set back in the axial direction and into which a centering ring formed on the mounting flange engages. On the one hand, a sealing ring can be arranged in the recessed area and, on the other hand, the adapter element can be precisely aligned and fastened to the housing cover in a fluid-tight manner.

Indem an der dem Montageflansch gegenüberliegenden Seite das Adapterelement mehrere Gewindelöcher zur Befestigung des Spalttopfes aufweist, ist es möglich, innerhalb einer Magnetkupplungsgröße unterschiedliche Spalttöpfe verschiedener Druckstufen bzw. Festigkeiten und/oder unterschiedlichen Werkstoffen zu verwenden bzw. auszutauschen.Since the adapter element has several threaded holes for fastening the containment shell on the side opposite the mounting flange, it is possible to use or exchange different containment shells of different pressure levels or strengths and/or different materials within one magnetic coupling size.

Erfindungsgemäß ist an der dem Montageflansch gegenüberliegenden Seite ein sich in axialer Richtung weiter in den Innenraum erstreckender Ring vorgesehen, der eine Anlaufsicherung bildet und eine Berührung des Außenrotors an dem Spalttopf verhindert.According to the invention, on the side opposite the mounting flange, there is a ring which extends further into the interior in the axial direction and which forms a start-up safeguard and prevents the outer rotor from touching the containment shell.

Zur Verbesserung der Strömungsführung des Mediums und zur einfacheren und somit kostengünstigen gießtechnischen Herstellung weist die Außenkontur des Adapterelementes einen im Wesentlichen konusförmigen Verlauf auf.In order to improve the flow guidance of the medium and for simpler and thus more cost-effective production by casting, the outer contour of the adapter element has an essentially conical shape.

Dabei verjüngt sich vorzugsweise das Adapterelement im Wesentlichen beginnend vom Montageflansch bis zum Ring.In this case, the adapter element preferably tapers essentially starting from the mounting flange up to the ring.

Nach einer weiteren Ausgestaltung ist vorgesehen, dass das in Richtung Gehäusedeckel weisende Ende des Außenrotors einen radial umlaufenden Vorsprung aufweist. Dadurch ist der radiale Abstand des Außenrotors zum Ring für den Normalbetrieb exakt herstellbar.According to a further embodiment, it is provided that the end of the outer rotor pointing in the direction of the housing cover has a radially circumferential projection. As a result, the radial distance between the outer rotor and the ring can be produced exactly for normal operation.

Aus dem gleichen Grund wird vorgeschlagen, dass, alternativ oder zusätzlich, der Vorsprung an der Innenseite des Ringes ausgebildet ist.For the same reason it is proposed that, alternatively or additionally, the projection is formed on the inside of the ring.

Bei einem weiteren Ausführungsbeispiel der Erfindung ist vorgesehen, dass das in Richtung Gehäusedeckel weisende Ende des Außenrotors einen Bereich mit reduziertem Außendurchmesser aufweist. Somit wird die Montierbarkeit des Adapterelementes bei kleinen Kupplungsdurchmessern gewährleistet.In a further exemplary embodiment of the invention, it is provided that the end of the outer rotor pointing in the direction of the housing cover has a region with a reduced outer diameter. This ensures that the adapter element can be assembled with small coupling diameters.

Bei einer weiteren vorteilhaften Ausgestaltung ist zwischen Laufrad und Innenrotor eine mit der um die Drehachse drehbar antreibbaren Laufradwelle in Wirkverbindung stehende Lageranordnung angeordnet.In a further advantageous refinement, a bearing arrangement which is in operative connection with the impeller shaft which can be driven in rotation about the axis of rotation is arranged between the impeller and the inner rotor.

Im Rahmen der Erfindung wird vorgeschlagen, dass bei einer weiteren Ausführungsform dass zwischen dem Innenrotor und der Lageranordnung eine Federeinrichtung angeordnet ist.Within the scope of the invention it is proposed that in a further embodiment a spring device is arranged between the inner rotor and the bearing arrangement.

Erfindungsgemäß befindet sich bei einer Ausführungsform zwischen der Federeinrichtung und dem Innenrotor eine auf die Laufradwelle aufgeschobene Distanzhülse, mittels der der Innenrotor in axialer Richtung tiefer in den Außenrotor gelangt. Damit sind die Magnete des Innenrotors und die Magnete des Außenrotors optimal zueinander ausgerichtet, um eine optimale Kraftübertragung von Außenrotor zu Innenrotor zu gewährleisten.According to the invention, in one embodiment between the spring device and the inner rotor there is a spacer sleeve pushed onto the impeller shaft, by means of which the inner rotor gets deeper into the outer rotor in the axial direction. The magnets of the inner rotor and the magnets of the outer rotor are thus optimally aligned with one another in order to ensure optimum power transmission from the outer rotor to the inner rotor.

Die Aufgabe der Erfindung wird ferner durch einen modularen Baukasten zur Herstellung einer erfindungsgemäßen Pumpenanordnung gelöst.The object of the invention is also achieved by a modular kit for producing a pump arrangement according to the invention.

Ausführungsbeispiele der Erfindung sind in den Zeichnungen dargestellt und werden im Folgenden näher beschrieben. Es zeigt die

Fig. 1
den Längsschnitt durch eine Magnetkupplungspumpenanordnung, die
Fig. 2
den Längsschnitt durch die Magnetkupplungspumpenanordnung gemäß Fig. 1 mit einem erfindungsgemäßen Adapterelement, die
Fig. 3
den Längsschnitt durch die Magnetkupplungspumpenanordnung gemäß Fig. 1 mit einem weiteren erfindungsgemäßen Adapterelement, die
Fig. 4
den Längsschnitt durch eine Magnetkupplungspumpenanordnung mit einer als Wärmesperre dienendem Gehäusedeckel und einem erfindungsgemäßen Adapterelement gemäß Fig. 2.
Exemplary embodiments of the invention are shown in the drawings and are described in more detail below. It shows the
1
the longitudinal section through a magnetic coupling pump assembly, the
2
according to the longitudinal section through the magnetic coupling pump arrangement 1 with an adapter element according to the invention, the
3
according to the longitudinal section through the magnetic coupling pump arrangement 1 with another adapter element according to the invention, the
4
according to the longitudinal section through a magnetic coupling pump arrangement with a housing cover serving as a heat barrier and an adapter element according to the invention 2 .

Die Fig. 1 zeigt eine Pumpenanordnung 1 in Form einer Magnetkupplungspumpenanordnung. Die Pumpenanordnung 1 weist ein mehrteiliges Pumpengehäuse 2 einer Kreiselpumpe auf, das ein als Spiralgehäuse ausgebildetes Hydraulikgehäuse 3, einen Gehäusedeckel 4, eine Lagerträgerlaterne 5, einen Lagerträger 6 und einen Lagerdeckel 7 umfasst.the 1 shows a pump arrangement 1 in the form of a magnetic coupling pump arrangement. The pump arrangement 1 has a multi-part pump housing 2 of a centrifugal pump, which includes a hydraulic housing 3 designed as a volute housing, a housing cover 4 , a bearing bracket lantern 5 , a bearing bracket 6 and a bearing cover 7 .

Das Hydraulikgehäuse 3 weist eine Einlassöffnung 8 zum Ansaugen eines Fördermediums und eine Auslassöffnung 9 zum Ausstoßen des Fördermediums auf. Der Gehäusedeckel 4 ist an der der Einlassöffnung 8 gegenüberliegenden Seite des Hydraulikgehäuses 3 angeordnet. An der dem Hydraulikgehäuse 3 abgewandten Seite des Gehäusedeckels 4 ist die Lagerträgerlaterne 5 befestigt. Der Lagerträger 6 ist an der dem Gehäusedeckel 4 gegenüberliegenden Seite der Lagerträgerlaterne 5 angebracht. Der Lagerdeckel 7 ist wiederum an der der Lagerträgerlaterne 5 abgewandten Seite des Lagerträgers 6 befestigt.The hydraulic housing 3 has an inlet opening 8 for sucking in a pumped medium and an outlet opening 9 for ejecting the pumped medium. The housing cover 4 is arranged on the side of the hydraulic housing 3 opposite the inlet opening 8 . The bearing bracket lantern 5 is attached to the side of the housing cover 4 facing away from the hydraulic housing 3 . The bearing carrier 6 is attached to the side of the bearing carrier lantern 5 opposite the housing cover 4 . The bearing cap 7 is in turn fastened to the side of the bearing carrier 6 facing away from the bearing carrier lantern 5 .

Ein Spalttopf 10 ist an der dem Hydraulikgehäuse 3 abgewandten Seite des Gehäusedeckels 4 befestigt und erstreckt sich zumindest teilweise durch einen vom Pumpengehäuse 2, insbesondere vom Gehäusedeckel 4, von der Lagerträgerlaterne 5 und von dem Lagerträger 6 begrenzten Innenraum 11. Der Spalttopf 10 weist einen im Wesentlichen zylindrischen Grundkörper 12 auf. Der Grundkörper 12 ist an einer Seite offen und an der der offenen Seite gegenüberliegenden Seite mittels eines gewölbten Bodens 13 geschlossen. An der offenen Seite ist ein ringartiger Befestigungsflansch 14 angeordnet, der einteilig mit dem Grundkörper 12 ausgebildet ist oder an diesen durch Schweißen oder mittels anderen geeigneten Befestigungsmitteln oder -vorrichtungen, beispielsweise Schrauben, Nieten oder dergleichen verbunden ist. Der Befestigungsflansch 14 liegt an der dem Innenraum 11 nahen Seite an einer Anlagefläche 15 des Gehäusedeckels 4 an und weist mehrere Montagelöcher 16 auf, durch die Schrauben 17 durchführbar und in im Gehäusedeckel 4 vorgesehene Gewindebohrungen 18 einschraubbar sind. Der Spalttopf 10 dichtet eine von ihm und dem Gehäusedeckel 4 umschlossene Kammer 19 hermetisch gegenüber dem Innenraum 11 ab.A containment shell 10 is attached to the side of the housing cover 4 facing away from the hydraulic housing 3 and extends at least partially through an interior space 11 delimited by the pump housing 2, in particular by the housing cover 4, by the bearing bracket lantern 5 and by the bearing bracket 6. The containment shell 10 has an im Substantially cylindrical body 12 on. The base body 12 is open on one side and closed on the side opposite the open side by means of a curved bottom 13 . Arranged on the open side is a ring-like fastening flange 14 which is formed in one piece with the base body 12 or is connected thereto by welding or by means of other suitable fastening means or devices, for example screws, rivets or the like. The mounting flange 14 rests on the side close to the interior 11 against a contact surface 15 of the housing cover 4 and has a plurality of mounting holes 16 through which screws 17 can be passed and screwed into threaded holes 18 provided in the housing cover 4 . The containment shell 10 hermetically seals a chamber 19 enclosed by it and the housing cover 4 from the interior 11 .

Eine um eine Drehachse A drehbare Laufradwelle 20 erstreckt sich von einer mittels des Hydraulikgehäuses 3 und des Gehäusedeckels 4 begrenzten Strömungskammer 21 durch eine in dem Gehäusedeckel 4 vorgesehene Öffnung 22 in die Kammer 19. An einem innerhalb der Strömungskammer 21 liegenden Wellenende der Laufradwelle 20 ist ein Laufrad 23 befestigt, am gegenüberliegenden Wellenende, das zwei Wellenabschnitte 20a, 20b mit sich jeweils vergrößernden Durchmessern aufweist, ist ein innerhalb der Kammer 19 angeordneter Innenrotor 24 vorgesehen. Der Innenrotor 24 ist mit mehreren Magneten 25 bestückt, die an der dem Spalttopf 10 zugewandten Seite des Innenrotors 24 angeordnet sind.An impeller shaft 20 rotatable about an axis of rotation A extends from a flow chamber 21 delimited by the hydraulic housing 3 and the housing cover 4 through an opening 22 provided in the housing cover 4 into the chamber 19 Impeller 23 attached, at the opposite end of the shaft, which has two shaft sections 20a, 20b, each with increasing diameters, an inner rotor 24 arranged within the chamber 19 is provided. The inner rotor 24 is fitted with a plurality of magnets 25 which are arranged on the side of the inner rotor 24 which faces the can 10 .

Zwischen Laufrad 23 und Innenrotor 24 ist eine mit der um die Drehachse A drehbar antreibbaren Laufradwelle 20 in Wirkverbindung stehende Lageranordnung 26 angeordnet. Ein koaxial zur Drehachse A angeordneter Lagerringträger 27, mit dem die stationären, d.h. die sich nicht mit der Laufradwelle 20 drehenden Teile der Lageranordnung 26 an ihrem Platz gehalten werden, liegt mit einem flanschartigen Bereich 28 an einer weiteren Anlagefläche 29 des Gehäusedeckels 4 an, ist mittels einer nicht dargestellten Schraubverbindung an dem Gehäusedeckel 4 befestigt und erstreckt sich in die Kammer 19.Arranged between the impeller 23 and the inner rotor 24 is a bearing arrangement 26 which is operatively connected to the impeller shaft 20 which can be driven so as to rotate about the axis of rotation A. A bearing ring carrier 27 arranged coaxially to the axis of rotation A, with which the stationary parts of the bearing arrangement 26, i.e. those parts that do not rotate with the impeller shaft 20, are held in place, has a flange-like area 28 on another contact surface 29 of the housing cover 4 attached to the housing cover 4 by means of a screw connection (not shown) and extends into the chamber 19.

Zwischen dem Innenrotor 24 bzw. dem Wellenabschnitt 20a und der Lageranordnung 26, insbesondere den sich mit der Laufradwelle 20 drehenden Teilen der Lageranordnung 26, ist eine Federeinrichtung 30 in Form eines Tellerfederpaketes angeordnet und beaufschlagt den Spannverbund, bestehend aus Laufrad 23, einer das Laufrad 23 über eine Scheibe 31 an die Laufradwelle 20 befestigende Laufradmutter 32, den sich mit der Laufradwelle 20 drehenden Teilen der Lageranordnung 26 und Innenrotor 24 mit einer Federkraft, derart, dass der Spannverbund, insbesondere über den Innenrotor 24, in einem gewissen Maße elastisch in Anlage an einer Anlagefläche 33 gehalten wird, die durch die unterschiedlichen Durchmesser der Wellenabschnitte 20a und 20b entsteht, wobei der Durchmesser des Wellenabschnittes 20b größer ist, als der Durchmesser des Wellenabschnittes 20a. Der Spannverbund umfasst also im Wesentlichen die sich mit der Laufradwelle 20 um die Drehachse A drehenden Bauteile.A spring device 30 in the form of a plate spring assembly is arranged between the inner rotor 24 or the shaft section 20a and the bearing arrangement 26, in particular the parts of the bearing arrangement 26 rotating with the impeller shaft 20, and acts on the clamping assembly, consisting of impeller 23, one impeller 23 impeller nut 32 fastened to the impeller shaft 20 via a disc 31, the parts of the bearing arrangement 26 rotating with the impeller shaft 20 and the inner rotor 24 with a spring force such that the clamping connection, in particular via the inner rotor 24, is held to a certain extent elastically in contact with a contact surface 33, which arises from the different diameters of the shaft sections 20a and 20b, the diameter of the shaft section 20b being larger than the diameter of the shaft section 20a. The clamping assembly thus essentially comprises the components rotating about the axis of rotation A with the impeller shaft 20 .

Ein nicht dargestellter Antriebsmotor, vorzugsweise ein Elektromotor, treibt eine Antriebswelle 34 an. Die um die Drehachse A antreibbare Antriebswelle 34 ist im Wesentlichen koaxial zur Laufradwelle 20 angeordnet. Die Antriebswelle 34 erstreckt sich durch den Lagerdeckel 7, den Lagerträger 6 und wenigstens teilweise in die Lagerträgerlaterne 5. Die Antriebswelle 34 ist in zwei in dem Lagerträger 6 untergebrachten Kugellagern 35, 36 gelagert. Am freien Ende der Antriebswelle 34 ist ein mehrere Magnete 37 tragender Außenrotor 38 angeordnet. Die Magnete 37 sind an der dem Spalttopf 10 zugewandten Seite des Außenrotors 38 angeordnet. Der Außenrotor 38 erstreckt sich zumindest teilweise über den Spalttopf 10 und wirkt mit dem Innenrotor 24 zusammen, derart, dass der rotierende Außenrotor 38 mittels magnetischer Kräfte den Innenrotor 24 und somit die Laufradwelle 20 und das Laufrad 23 ebenfalls in eine Rotationsbewegung versetzt.A drive motor, not shown, preferably an electric motor, drives a drive shaft 34 . The drive shaft 34 , which can be driven about the axis of rotation A, is arranged essentially coaxially with the impeller shaft 20 . The drive shaft 34 extends through the bearing cover 7, the bearing bracket 6 and at least partially into the bearing bracket lantern 5. The drive shaft 34 is mounted in two ball bearings 35, 36 accommodated in the bearing bracket 6. At the free end of the drive shaft 34 there is an outer rotor 38 carrying a plurality of magnets 37 . The magnets 37 are arranged on the side of the outer rotor 38 facing the can 10 . The outer rotor 38 extends at least partially over the containment shell 10 and interacts with the inner rotor 24 in such a way that the rotating outer rotor 38 also causes the inner rotor 24 and thus the impeller shaft 20 and the impeller 23 to rotate by means of magnetic forces.

Die Fig. 2 zeigt eine Pumpenanordnung 1, deren Außenmaße den in der Fig. 1 gezeigten Außenmaßen entsprechen. Gemäß eines Baukastenprinzips weisen Hydraulikgehäuse 3, Gehäusedeckel 4, Lagerträgerlaterne 5, Lagerträger 6 und Lagerdeckel 7 also eine gleichgroße Dimensionierung auf. Außerdem weisen in beiden Ausführungsformen Laufrad 23, Lageranordnung 26 und Lagerringträger 27 eine gleiche Dimensionierung auf. Bei der in der Fig. 2 gezeigten Ausführungsform sind sowohl Durchmesser als auch axiale Erstreckung von Spalttopf 10, Innenrotor 24 und Außenrotor 38 geringer als bei der in der Fig. 1 gezeigten Ausführungsform. Dies ist besonders vorteilhaft, wenn kleinere Leistungsanforderungen, beispielsweise eine geringere Förderhöhe oder Fördermenge, bei höchstmöglicher Effizienz an die Pumpenanordnung 1 bestehen.the 2 shows a pump assembly 1, whose external dimensions in the 1 correspond to the external dimensions shown. According to a modular principle, the hydraulic housing 3, the housing cover 4, the bearing bracket lantern 5, the bearing bracket 6 and the bearing cap 7 have the same dimensions. In addition, impeller 23, bearing arrangement 26 and bearing ring carrier 27 have the same dimensions in both embodiments. At the in the 2 The embodiment shown are both the diameter and the axial extent of the can 10, the inner rotor 24 and the outer rotor 38 are smaller than in the case of FIG 1 embodiment shown. This is particularly advantageous when the pump arrangement 1 has lower performance requirements, for example a lower delivery height or delivery quantity, with the highest possible efficiency.

Zum Anpassen des Spalttopfes 10 mit verringerter axialer Erstreckung und vermindertem Durchmesser ist ein separates Adapterelement 39 vorgesehen, das auf einer Seite einen Montageflansch 40 aufweist, dessen Ausgestaltung im Wesentlichen der Ausgestaltung des in der Fig. 1 gezeigten Befestigungsflansches 14 des Spalttopfes 10 entspricht. Der Montageflansch 40 liegt an der dem Innenraum 11 nahen Seite an der Anfagefläche 15 des Gehäusedeckels 4 an und weist mehrere Montagelöcher 41 auf, durch die die Schrauben 17 durchführbar und in die im Gehäusedeckel 4 vorgesehenen Gewindebohrungen 18 einschraubbar sind. Die Anlagefläche 15 weist einen in axialer Richtung zurückgesetzten Bereich 42 auf, in dem ein Dichtungsring 43 angeordnet ist und in den ein an dem Montageflansch 40 ausgebildeter Zentrierring 44 eingreift, wodurch das Adapterelement 39 exakt ausgerichtet und fluiddicht an dem Gehäusedeckel 4 befestigbar ist.A separate adapter element 39 is provided for adapting the containment shell 10 with a reduced axial extension and a reduced diameter, on one side has a mounting flange 40, the configuration of which is substantially the same as that in the 1 shown mounting flange 14 of the containment shell 10 corresponds. The mounting flange 40 rests against the contact surface 15 of the housing cover 4 on the side close to the interior 11 and has a plurality of mounting holes 41 through which the screws 17 can be passed and screwed into the threaded holes 18 provided in the housing cover 4 . The contact surface 15 has a region 42 set back in the axial direction, in which a sealing ring 43 is arranged and in which a centering ring 44 formed on the mounting flange 40 engages, as a result of which the adapter element 39 can be precisely aligned and fastened to the housing cover 4 in a fluid-tight manner.

An der dem Montageflansch 40 gegenüberliegenden Seite weist das Adapterelement 39 mehrere Gewindelöcher 45 auf, in welche sich durch die Montagelöcher 16 im Befestigungsflansch 14 des Spalttopfes 10 erstreckende Schrauben 46 einschraubbar sind. Damit ist es möglich, innerhalb einer Magnetkupplungsgröße unterschiedliche Spalttöpfe 10 verschiedener Druckstufen bzw. Festigkeiten und/oder unterschiedlichen Werkstoffen auszutauschen. Außerdem ist an der dem Montageflansch 40 gegenüberliegenden Seite ein sich in axialer Richtung weiter in den Innenraum 11 erstreckender Ring 47 vorgesehen, der eine Anlaufsicherung bildet und eine Berührung der Magnete 37 des Außenrotors 38 an dem Grundkörper 12 des Spalttopfes 10 verhindert. Die Außenkontur des Adapterelementes 39 weisen jeweils einen im Wesentlichen konusförmigen Verlauf auf. Beginnend im Wesentlichen vom Montageflansch 40 verjüngt sich dabei das Adapterelement 39 bis zum Ring 47. Die Innenkontur des Adapterelementes 39 ist zumindest sich teilweise verjüngend ausgebildet. Bei der in der Fig. 2 dargestellten Ausführungsform weist das in Richtung Gehäusedeckel 4 weisende Ende des Außenrotors 38 einen dem Ring 47 zugewandten radial umlaufenden Vorsprung 48 auf, der bei einem möglicherweise mit einer Unwucht drehenden Außenrotor 38 in jedem Fall zuerst die Innenseite des Ringes 47 des Adapterelementes 39 berührt, bevor die Magnete 37 des Außenrotors 38 in Kontakt mit dem Grundkörper 12 des Spalttopfes 10 kommen. Bei einer alternativen Ausführungsform kann der Vorsprung 48 auch an der Innenseite des Ringes 47 ausgebildet sein. Bei einer weiteren Ausführungsform kann der Vorsprung 48 sowohl am Ende des Außenrotors 38 als auch an der Innenseite des Ringes 47 ausgebildet sein.On the side opposite the mounting flange 40, the adapter element 39 has a plurality of threaded holes 45 into which screws 46 extending through the mounting holes 16 in the mounting flange 14 of the containment shell 10 can be screwed. This makes it possible to exchange different containment shells 10 of different pressure stages or strengths and/or different materials within one magnetic coupling size. In addition, on the side opposite the mounting flange 40 there is a ring 47 which extends further into the interior 11 in the axial direction and which forms a safety device and prevents the magnets 37 of the outer rotor 38 from touching the base body 12 of the containment shell 10 . The outer contour of the adapter element 39 each have an essentially conical shape. Starting essentially from the mounting flange 40, the adapter element 39 tapers down to the ring 47. The inner contour of the adapter element 39 is at least partially tapered. At the in the 2 In the embodiment shown, the end of the outer rotor 38 pointing in the direction of the housing cover 4 has a radially circumferential projection 48 facing the ring 47, which in any case first touches the inside of the ring 47 of the adapter element 39 if the outer rotor 38 is possibly rotating with an imbalance before the Magnets 37 of the outer rotor 38 come into contact with the base body 12 of the containment shell 10 . In an alternative embodiment, the projection 48 can also be formed on the inside of the ring 47 . In another embodiment the projection 48 can be formed both at the end of the outer rotor 38 and on the inside of the ring 47.

Zwischen der Federeinrichtung 30 und dem Innenrotor 24 befindet sich eine auf die Laufradwelle 20 aufgeschobene Distanzhülse 49, die den vorstehend beschriebenen Spannverbund um dieses Bauteil erweitert. Bei der gezeigten Ausführungsform ist die Laufradwelle 20, insbesondere Wellenabschnitt 20a, um die Länge der Distanzhülse 49 gegenüber der in der Fig. 1 gezeigten Ausführungsform verlängert. Mittels der Distanzhülse 49 gelangt der Innenrotor 24 in axialer Richtung tiefer in den Außenrotor 38. Damit sind die Magnete 25 des Innenrotors 24 und die Magnete 37 des Außenrotors 38 optimal zueinander ausgerichtet, um eine optimale Kraftübertragung von Außenrotor 38 zu Innenrotor 24 zu gewährleisten.Between the spring device 30 and the inner rotor 24 there is a spacer sleeve 49 which is pushed onto the impeller shaft 20 and expands the above-described clamping assembly by this component. In the embodiment shown, the impeller shaft 20, in particular shaft section 20a, is by the length of the spacer sleeve 49 compared to that in FIG 1 embodiment shown extended. The inner rotor 24 moves deeper into the outer rotor 38 in the axial direction by means of the spacer sleeve 49. The magnets 25 of the inner rotor 24 and the magnets 37 of the outer rotor 38 are thus optimally aligned with one another in order to ensure optimal power transmission from the outer rotor 38 to the inner rotor 24.

Die Fig. 3 zeigt eine Pumpenanordnung 1, deren Außenmaße den in den Fig. 1 und Fig. 2 gezeigten Außenmaßen entsprechen. Ebenso weisen Laufrad 23, Lageranordnung 26 und Lagerringträger 27 eine gleiche Dimensionierung, wie bei den in den Fig. 1 und 2 gezeigten Ausführungsformen, auf. Bei der in der Fig. 3 gezeigten Ausführungsform sind sowohl Durchmesser als auch axiale Erstreckung von Spalttopf 10, Innenrotor 24 und Außenrotor 38 gegenüber der in der Fig. 2 gezeigten Ausführungsform weiter verringert worden. Die Laufradwelle 20, insbesondere Wellenabschnitt 20a, weist die selbe axiale Erstreckung auf, wie bei der in der Fig. 2 gezeigten Ausführungsform. Das in Richtung Gehäusedeckel 4 weisende Ende des Außenrotors 38 weist einen dem Ring 47 zugewandten Bereich 50 mit reduziertem Außendurchmesser auf, mit dem ein möglicherweise sich mit einer Unwucht drehender Außenrotor 38 in jedem Fall zuerst an die Innenseite des Ringes 47 des Adapterelementes 39 in Anlage gerät, bevor die Magnete 37 des Außenrotors 38 in Kontakt mit dem Grundkörper 12 des Spalttopfes 10 kommen.the 3 shows a pump assembly 1, whose external dimensions in the 1 and 2 correspond to the external dimensions shown. Likewise, impeller 23, bearing assembly 26 and bearing ring carrier 27 have the same dimensions as in the 1 and 2 embodiments shown on. At the in the 3 The embodiment shown are both the diameter and the axial extent of containment shell 10, inner rotor 24 and outer rotor 38 compared to that in FIG 2 embodiment shown has been further reduced. The impeller shaft 20, in particular shaft section 20a, has the same axial extent as in the case of FIG 2 embodiment shown. The end of the outer rotor 38 pointing in the direction of the housing cover 4 has an area 50 facing the ring 47 with a reduced outer diameter, with which an outer rotor 38 possibly rotating with an imbalance first comes into contact with the inside of the ring 47 of the adapter element 39 , before the magnets 37 of the outer rotor 38 come into contact with the base body 12 of the can 10.

Wie aus der Fig. 4 ersichtlich, kann das Adapterelement 39 auch an einem als Wärmesperre ausgebildeten Gehäusedeckel 4 bei einer ein heißes Medium führenden Pumpenanordnung 1 verwendet werden. Dabei weisen das Hydraulikgehäuse 3, wesentliche Bereiche des Gehäusedeckels 4, Lagerträgerlaterne 5, Lagerträger 6 und Lagerdeckel 7 eine gleiche Dimensionierung wie bei den in den Fig. 1 bis 3 gezeigten Ausführungsbeispielen auf. Der Spalttopf 10, das Adapterelement 39 und der Außenrotor 38 weisen eine gleiche Dimensionierung entsprechend der Magnetkupplungsgröße gemäß Fig. 2 auf. Bezuqszeichenliste 1 Pumpenanordnung 27 Lagerringträger 2 Pumpengehäuse 28 flanschartigen Bereich 3 Hydraulikgehäuse 29 Anlagefläche 4 Gehäusedeckel 30 Federeinrichtung 5 Lagerträgerlaterne 31 Scheibe 6 Lagerträger 32 Laufradmutter 7 Lagerdeckel 33 Anlagefläche 8 Einlassöffnung 34 Antriebswelle 9 Auslassöffnung 35 Kugellager 10 Spalttopf 36 Kugellager 11 Innenraum 37 Magnet 12 Grundkörper 38 Außenrotor 13 Boden 39 Adapterelement 14 Befestigungsflansch 40 Montageflansch 15 Anlagefläche 41 Montageloch 16 Montageloch 42 zurückgesetzter Bereich 17 Schraube 43 Dichtungsring 18 Gewindebohrung 44 Zentrierring 19 Kammer 45 Gewindeloch 20 Laufradwelle 46 Schraube 20a Wellenabschnitt 47 Ring 20b Wellenabschnitt 48 Vorsprung 21 Strömungskammer 49 Distanzhülse 22 Öffnung 50 Bereich mit reduziertem Außendurchmesser 23 Laufrad 24 Innenrotor 25 Magnet A Drehachse 26 Lageranordnung How from the 4 As can be seen, the adapter element 39 can also be used on a housing cover 4 designed as a heat barrier in a pump arrangement 1 carrying a hot medium. Here, the hydraulic housing 3, major areas of the housing cover 4, bearing bracket lantern 5, bearing bracket 6 and bearing cap 7 have the same dimensions as in the Figures 1 to 3 shown embodiments on. The containment shell 10, the adapter element 39 and the outer rotor 38 have the same dimensions according to the size of the magnetic coupling 2 on. <u>Reference Character List</u> 1 pump arrangement 27 bearing ring carrier 2 pump housing 28 flange-like area 3 hydraulic housing 29 contact surface 4 housing cover 30 spring device 5 Quill Lantern 31 disc 6 bearing carrier 32 impeller nut 7 bearing cap 33 contact surface 8th intake port 34 drive shaft 9 exhaust port 35 ball-bearing 10 containment shell 36 ball-bearing 11 inner space 37 magnet 12 body 38 outer rotor 13 floor 39 adapter element 14 mounting flange 40 mounting flange 15 contact surface 41 mounting hole 16 mounting hole 42 reset area 17 screw 43 sealing ring 18 threaded hole 44 centering ring 19 chamber 45 threaded hole 20 impeller shaft 46 screw 20a wave section 47 ring 20b wave section 48 head Start 21 flow chamber 49 spacer sleeve 22 opening 50 Area with reduced outer diameter 23 Wheel 24 inner rotor 25 magnet A axis of rotation 26 bearing arrangement

Claims (13)

  1. Modular construction kit for structural size configuration for one hydraulic size with different magnetic coupling sizes, or for one magnetic coupling size and different hydraulic sizes, for producing a pump arrangement having an interior space (11) formed by a pump casing (2) of the pump arrangement (1), having a containment can (10) which hermetically seals off a chamber (19) surrounded by said containment can with respect to the interior space (11) formed by the pump casing (2), having an impeller shaft (20) which can be driven in rotation about an axis of rotation (A), having an impeller (23) which is arranged on one end of the impeller shaft (20), having an inner rotor (24) which is arranged on the other end of the impeller shaft (20), and having an outer rotor (38) which interacts with the inner rotor (24),
    characterized by
    different adaptor elements (39) connecting the containment can (10) to a casing cover (4) of the pump casing (2), which adaptor elements have a mounting flange (40) which, at the side close to the interior space (11), bears against an abutment surface (15) of the casing cover (4).
  2. Pump arrangement for structural size configuration for one hydraulic size with different magnetic coupling sizes, or for one magnetic coupling size and different hydraulic sizes, for a modular construction kit according to Claim 1, having an interior space (11) formed by a pump casing (2) of the pump arrangement (1), a containment can (10) which hermetically seals off a chamber (19) surrounded by said containment can with respect to the interior space (11) formed by the pump casing (2), an impeller shaft (20) which can be driven in rotation about an axis of rotation (A), an impeller (23) which is arranged on one end of the impeller shaft (20), an inner rotor (24) which is arranged on the other end of the impeller shaft (20), and an outer rotor (38) which interacts with the inner rotor (24),
    characterized by
    different adaptor elements (39) connecting the containment can (10) to a casing cover (4) of the pump casing (2), which adaptor elements have a mounting flange (40) which, at the side close to the interior space (11), bears against an abutment surface (15) of the casing cover (4).
  3. Pump arrangement according to Claim 2, characterized in that the abutment surface (15) has a region (42) which is recessed in an axial direction and into which a centring ring (44) formed on the mounting flange (40) engages.
  4. Pump arrangement according to Claim 2 or 3, characterized in that, on the side situated opposite the mounting flange (40), the adaptor element (39) has multiple threaded holes (45).
  5. Pump arrangement according to one of Claims 2 to 4, characterized in that, on the side situated opposite the mounting flange (40), a ring (47) which extends further in the axial direction into the interior space (11) is provided.
  6. Pump arrangement according to one of Claims 2 to 5, characterized in that the outer contour of the adaptor element (39) has a substantially conical profile.
  7. Pump arrangement according to Claim 6, characterized in that, proceeding from the mounting flange (40), the adaptor element (39) narrows towards the ring (47) .
  8. Pump arrangement according to one of Claims 2 to 7, characterized in that that end of the outer rotor (38) which points in the direction of the casing cover (4) has a radially encircling projection (48).
  9. Pump arrangement according to one of Claims 2 to 8, characterized in that the projection (48) is formed on the inner side of the ring (47).
  10. Pump arrangement according to one of Claims 2 to 7, characterized in that that end of the outer rotor (38) which points in the direction of the casing cover (4) has a region (50) of reduced outer diameter.
  11. Pump arrangement according to one of Claims 2 to 10, characterized in that, between the impeller (23) and inner rotor (24), there is arranged a bearing arrangement (26) which is operatively connected to the impeller shaft (20), which can be driven in rotation about the axis of rotation (A).
  12. Pump arrangement according to Claim 11, characterized in that a spring device (30) is arranged between the inner rotor (24) and the bearing arrangement (26).
  13. Pump arrangement according to Claim 12, characterized in that, between the spring device (30) and the inner rotor (24), there is situated a spacer sleeve (49) which is pushed onto the impeller shaft (20).
EP14726122.6A 2013-05-24 2014-05-19 Pump arrangement Active EP3004649B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102013008795.3A DE102013008795B3 (en) 2013-05-24 2013-05-24 pump assembly
PCT/EP2014/060197 WO2014187761A1 (en) 2013-05-24 2014-05-19 Pump arrangement

Publications (2)

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EP3004649A1 EP3004649A1 (en) 2016-04-13
EP3004649B1 true EP3004649B1 (en) 2022-05-11

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EP14726122.6A Active EP3004649B1 (en) 2013-05-24 2014-05-19 Pump arrangement

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US (1) US10385860B2 (en)
EP (1) EP3004649B1 (en)
JP (1) JP6491196B2 (en)
KR (1) KR102125989B1 (en)
AU (1) AU2014270523C1 (en)
BR (1) BR112015029322B1 (en)
DE (1) DE102013008795B3 (en)
ES (1) ES2922414T3 (en)
RU (1) RU2670369C2 (en)
SG (1) SG11201509124PA (en)
WO (1) WO2014187761A1 (en)
ZA (1) ZA201508250B (en)

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Also Published As

Publication number Publication date
SG11201509124PA (en) 2015-12-30
KR102125989B1 (en) 2020-07-08
WO2014187761A1 (en) 2014-11-27
US20160108923A1 (en) 2016-04-21
KR20160012136A (en) 2016-02-02
BR112015029322A2 (en) 2017-07-25
AU2014270523B2 (en) 2017-04-20
BR112015029322B1 (en) 2022-03-08
ZA201508250B (en) 2017-01-25
EP3004649A1 (en) 2016-04-13
ES2922414T3 (en) 2022-09-14
RU2670369C2 (en) 2018-10-22
DE102013008795B3 (en) 2014-08-21
JP2016519252A (en) 2016-06-30
CN105431637A (en) 2016-03-23
RU2015148040A (en) 2017-06-28
AU2014270523A1 (en) 2015-11-26
US10385860B2 (en) 2019-08-20
AU2014270523C1 (en) 2017-07-20
JP6491196B2 (en) 2019-03-27

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