EP2994641A1 - Pump arrangement - Google Patents

Pump arrangement

Info

Publication number
EP2994641A1
EP2994641A1 EP14719796.6A EP14719796A EP2994641A1 EP 2994641 A1 EP2994641 A1 EP 2994641A1 EP 14719796 A EP14719796 A EP 14719796A EP 2994641 A1 EP2994641 A1 EP 2994641A1
Authority
EP
European Patent Office
Prior art keywords
external thread
pump arrangement
hub
pump
drive shaft
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
EP14719796.6A
Other languages
German (de)
French (fr)
Other versions
EP2994641B1 (en
Inventor
Patrick Drechsel
Markus Lay
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.)
KSB SE and Co KGaA
Original Assignee
KSB AG
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 KSB AG filed Critical KSB AG
Publication of EP2994641A1 publication Critical patent/EP2994641A1/en
Application granted granted Critical
Publication of EP2994641B1 publication Critical patent/EP2994641B1/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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
    • F04D13/06—Units comprising pumps and their driving means the pump being electrically driven
    • F04D13/0606—Canned motor pumps
    • F04D13/064—Details of the magnetic circuit
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D1/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • 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
    • F04D13/025—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
    • F04D13/06—Units comprising pumps and their driving means the pump being electrically driven
    • F04D13/0606—Canned motor pumps
    • F04D13/0613—Special connection between the rotor compartments
    • 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
    • F04D13/06—Units comprising pumps and their driving means the pump being electrically driven
    • F04D13/0606—Canned motor pumps
    • F04D13/0626—Details of the can
    • 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
    • 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
    • F04D29/00—Details, component parts, or accessories
    • F04D29/04—Shafts or bearings, or assemblies thereof
    • F04D29/043—Shafts
    • F04D29/044—Arrangements for joining or assembling shafts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
    • F04D29/053—Shafts
    • F04D29/054—Arrangements for joining or assembling shafts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/18—Rotors
    • F04D29/22—Rotors specially for centrifugal pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/58—Cooling; Heating; Diminishing heat transfer
    • F04D29/586—Cooling; Heating; Diminishing heat transfer specially adapted for liquid pumps
    • F04D29/5893—Cooling; Heating; Diminishing heat transfer specially adapted for liquid pumps heat insulation or conduction

Definitions

  • the invention relates to a pump arrangement, in particular Magnetkupplungspumpen- arrangement, with a housing formed by a pump housing of the pump assembly, a split pot which hermetically seals a chamber enclosed by him against the interior formed by the pump housing, a rotatable about an axis of rotation driven impeller shaft, one at one End of the impeller shaft arranged impeller, arranged at the other end of the impeller shaft inner rotor, a drive motor, a drive shaft rotatably driven by the drive motor about the axis of rotation drive shaft and arranged on the drive shaft, cooperating with the inner rotor outer rotor, wherein the outer rotor as a hub comprises a first carrier element.
  • Explosion-proof block motors in particular standard motors in flange design, allow only a certain heat input into the motor at the interfaces, in particular flange and shaft, such that the maximum permissible temperatures of the motor are not exceeded.
  • the object of the invention is to provide a pump assembly which allows for increased temperature of the medium to be delivered, while maintaining the explosion protection of the drive motor, a reduction of the axial and radial space and ease of assembly.
  • the object of the invention is achieved in that the outer rotor between the hub and the first support member has a hollow cylindrical portion. Characterized in that the hub is not disposed directly on the first support member, but the hollow cylinder-like portion is connected downstream of the drive shaft, the heat input is reduced by the outer magnet carrier in the drive shaft and thus in the drive motor.
  • the hollow-cylindrical portion and the hub with respect to the first support member are formed thin-walled.
  • the hollow cylindrical portion and the hub each have a wall with a certain wall thickness, wherein the wall thickness of the wall of the hollow cylindrical portion and the wall thickness of the wall of the hub is smaller than the radius of the drive shaft and chosen so that in each case a safe torsion - And bending fatigue strength is guaranteed. This leads to a further reduction of the heat input from the outer magnet carrier in the drive shaft of the drive motor.
  • An advantageous embodiment provides that the axial fixing of the outer magnetic carrier takes place on the drive shaft by a fastening element.
  • the fastening element has a first external thread at one end and a second external thread at the end opposite the first external thread, wherein a spacer holding section is located between the first external thread and the second external thread whose outer diameter is greater than the outer diameter of the first external thread and second external thread.
  • the spacer section on the side close to the first external thread has a collar with an enlarged outside diameter, as a result of which the fastening element can be positioned exactly axially and fastened in an uncomplicated manner.
  • the spacer portion on the side close to the first external thread may taper conically.
  • a radial threaded bore is formed in the hub into which a screw is screwed.
  • Fig. 1 shows a longitudinal section through a magnetic coupling pump assembly with an external rotor according to the invention
  • FIG. 2 is an enlarged view of an outer rotor corresponding to FIG. 1, and FIG. 3 is a section along the line III-III of FIG. 2.
  • FIG. 1 shows a pump arrangement 1 in the form of a magnetic coupling pump arrangement with a pump part and an electrical part.
  • the pump part of the pump arrangement 1 has a multipart pump housing 2 of a centrifugal pump, which comprises a hydraulic housing 3 designed as a spiral housing, a housing cover 4, a bearing support lantern 5 and a connecting element 6.
  • the hydraulic housing 3 has an inlet opening 7 for sucking in a conveyed medium and an outlet opening 8 for ejecting the conveyed medium.
  • the housing cover 4 is arranged on the side of the hydraulic housing 3 opposite the inlet opening 7. On the side facing away from the hydraulic housing 3 of the
  • the bearing bracket lantern 5 is attached.
  • the connecting element 6 is attached to the housing cover 4 opposite side of the bearing bracket lantern 5.
  • a drive motor 9 forming the electrical part is arranged on the opposite side of the bearing support lantern 5.
  • a containment shell 10 is fastened to the side of the housing cover 4 facing away from the hydraulic housing 3 and extends at least partially through an inner space 11 bounded by the pump housing 2, in particular by the housing cover 4, by the bearing support lantern 5 and by the connecting element 6.
  • the containment shell 10 seals one of enclosed chamber 12 hermetically against the interior 11 from.
  • a rotatable impeller shaft 13 extends from a limited by means of the hydraulic housing 3 and the housing cover 4 flow chamber 14 through an opening provided in the housing cover 4 opening 15 into the chamber 12.
  • an impeller 16 fixed at the opposite shaft end, which has two shaft portions 13a, 13b each with increasing diameters, an arranged inside the chamber 12 inner rotor 17 is arranged.
  • the inner rotor 17 is equipped with a plurality of magnets 18, which are arranged on the side of the inner rotor 17 facing the spit pot 10.
  • a bearing assembly 19 operatively connected to the impeller wheel 13 rotatably driven about the axis of rotation A is arranged.
  • the drive motor 9 comprises a drive shaft 20.
  • the drive shaft 20 which can be driven about the axis of rotation A is arranged essentially coaxially to the rotor shaft 13.
  • the drive shaft 20 extends into the connecting element 6 and possibly at least partially into the bearing support lantern 5.
  • a plurality of magnets 21 supporting outer rotor 22 is arranged.
  • the magnets 21 are arranged on the side of the outer rotor 22 facing the containment shell 10.
  • the outer rotor 22 extends at least partially over the containment shell 10 and interacts with the inner rotor 17 together, such that the rotating outer rotor 22 mitteis magnetic forces the inner rotor 17 and thus the impeller shaft 13 and the impeller 16 also set in a rotational movement.
  • the outer rotor 22 shown enlarged in FIG. 2 comprises a hub 23 with an outer circumferential surface 24, a hollow cylindrical portion 25 formed on the side of the hub 23 facing away from the drive motor 9 with a cell 27 bounded by a wall 26.
  • the outer rotor 22 further comprises a at the side facing the gap pot 10 side of the hollow cylinder-like portion 25 formed or angeordne- tes first support member 28 and a formed on the first support member 28 hollow cylinder-like second support member 29 which at least partially surrounds the can 10 and on which the magnets 21 are arranged ,
  • First and second support members 28, 29 are shown as two interconnectable parts, but may also be made as one part.
  • the hollow-cyan-like section 25 has a wall 25a with a wall thickness S1 and the hub 23 has a wall 23a with a wall thickness S2.
  • the hollow-cylinder-like portion 25 and the hub 23 are formed thin-walled with respect to the first support member 28.
  • the wall thicknesses S1, S2 are substantially smaller than the thickness d1 of the first carrier element 28.
  • the wall thickness S1 of the wall 25a of the hollow cylinder-like portion 25 and the wall thickness S2 of the wall 23a of the hub 23 are chosen such that in each case a safe Torsions- and bending fatigue strength is ensured.
  • the wall thicknesses S1, S2 are also smaller than the radius r of the drive shaft 20.
  • the wall thickness S1 of the wall 25a is smaller than the wall thickness S2 of the wall 23a.
  • a through hole 30 extends into the cell 27 of the arranged between the hub 23 and the first support member 28 hollow cylindrical portion 25 and forms a hub inner surface 31.
  • the hub inner surface 31 is a parallel to the axis of rotation
  • a extending axial groove 32 is provided in the hub inner surface 31 .
  • a keyway 33 oriented toward the axial groove 32 is formed, into which the motor torque is transmitted to the hub 23 of the outer rotor 22 a feather key 34 is inserted.
  • the axial fixing of the outer rotor 22 to the drive shaft 20 is effected by a fastening element 35.
  • the fastening element 35 has at one end a first external thread 37 which can be screwed into a threaded bore 36 formed coaxially with the rotation axis A on the end face of the drive shaft 20, and a second external thread 38 at the end opposite the first external thread 37. Between the first external thread 37 and the second external thread 38, a spacer holding portion 39 is formed, the outer diameter of which is greater than the outer diameter of the first external thread 37 and the second external thread 38.
  • the fastening element 35 is screwed into the threaded bore 36 with the first external thread 37 until the spacer holding section 39 comes into contact with the end face of the drive shaft 20.
  • the spacer holding portion 39 on the first external thread 37 side near a collar 40 with an enlarged outer diameter, which rests against the drive shaft 20.
  • the collar 40 is preferably listed as a hexagon or has at least two key surfaces.
  • the spacer holding section 39 on the side close to the first external thread 37 may taper conically and come into abutment with the conical inlet region of the threaded bore 36.
  • the second external thread 38 extends through an opening 41 in the wall 26, wherein the spacer holding portion 39 of the fastening element 35 is in contact with the wall 26. With a screwed onto the second external thread 38 nut 42, the axial fixing of the outer rotor 22 takes place on the drive shaft 20.
  • the outer rotor 22 is in this way axially accurately positioned and fastened in a simple manner.
  • a through hole 43 extends from one end face of the fastener 35 to the other to keep the heat transferring the heat from the outer rotor 22 into the drive shaft 20 as small as possible.
  • a blind hole can be provided, which extends either from the first external thread 37 near end face extends close to or in the Distanzhalteabschnttt 39 or from the second external thread 38 near the end face to the collar 40 or beyond.
  • FIG. 3 shows that a radial threaded bore 44 is formed in the hub 23, into which a screw element 45, in particular grub screw, is screwed.
  • the drive shaft 20 facing the end of the screw 45 is preferably formed like a truncated cone.
  • the threaded bore 44 is always in Dehraum the driven drive shaft 20, which is indicated here by the arrow M, at an angle ⁇ of about 35 ° to about 55 ° and preferably at an angle ⁇ of 40 ° to 50 ° and preferably at an angle ⁇ of about 45 ° to the axial groove 32 is arranged. If necessary, there are further, not shown, threaded holes 44 in the hub 23 along its axial extent.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Details Of Reciprocating Pumps (AREA)
  • Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)

Abstract

The invention relates to a pump arrangement (1), more particularly a magnetic clutch pump arrangement, comprising an inner chamber (11) formed by a pump housing (2) in the pump arrangement (1); a containment shell (10) which hermetically seals an enclosed chamber (12) with respect to the inner chamber (11) formed by the pump housing (2); an impeller shaft (13) that can be driven in rotation about an axis of rotation (A); an impeller (16) mounted on one end of the impeller shaft (13); an inner rotor (17) mounted on the other end of the impeller shaft (13); a drive motor (9); a drive shaft (20) that can be driven in rotation about the axis of rotation (A) by the drive motor (9); and an outer rotor (22) which is mounted on the drive shaft (20) and co-operates with the inner rotor (17); wherein the outer rotor (22) has a hub (23) and a first support element (28). According to the invention the outer rotor (22) has a hollow cylindrical portion (25) between the hub (23) and the first support element (28).

Description

Beschreibung  description
Pumpenanordnung pump assembly
Die Erfindung betrifft eine Pumpenanordnung, insbesondere Magnetkupplungspumpen- anordnung, mit einem von einem Pumpengehäuse der Pumpenanordnung gebildeten Innenraum, einem Spalttopf, der eine von ihm umschlossene Kammer hermetisch gegenüber dem vom Pumpengehäuse gebildeten Innenraum abdichtet, einer um eine Drehachse drehbar antreibbaren Laufradwelle, einem an einem Ende der Laufradwelle angeordneten Laufrad, einem an dem anderen Ende der Laufradwelle angeordneten Innenrotor, einem Antriebsmotor, einer von dem Antriebsmotor drehbar um die Drehachse antreibbare Antriebswelle und einem auf der Antriebswelle angeordneten, mit dem Innenrotor zusammenwirkenden Außenrotor, wobei der Außenrotor eine Nabe so- wie ein erstes Trägerelement aufweist. The invention relates to a pump arrangement, in particular Magnetkupplungspumpen- arrangement, with a housing formed by a pump housing of the pump assembly, a split pot which hermetically seals a chamber enclosed by him against the interior formed by the pump housing, a rotatable about an axis of rotation driven impeller shaft, one at one End of the impeller shaft arranged impeller, arranged at the other end of the impeller shaft inner rotor, a drive motor, a drive shaft rotatably driven by the drive motor about the axis of rotation drive shaft and arranged on the drive shaft, cooperating with the inner rotor outer rotor, wherein the outer rotor as a hub comprises a first carrier element.
Derartige Pumpenanordnungen sind weit verbreitet und finden in nahezu allen Bereichen der Industrie ihre Anwendung. Maschinen der vorliegenden Art werden auch in explosionsgefährdeten Bereichen eingesetzt. Für die verschiedenen Produktions- und Förderanlagen, insbesondere im Bereich der Chemie, existieren besondere Vorschriften im Zusammenhang mit dem Explosionsschutz. In solchen Anlagen finden einerseits Arbeitsmaschinen, beispielsweise Pumpen oder Turbinen, als nicht elektrische Geräte, und andererseits Kraftmaschinen, beispielsweise Antriebsmotoren, als elektrische Geräte, Verwendung. Für elektrische Geräte existieren seit langem bewährte Sicherheits- Standards. In diesen Standards ist festgeschrieben, welche baulichen Maßnahmen zu treffen sind, um ein elektrisches Gerät in den verschiedenen explosionsgefährdeten Bereichen einsetzen zu können. Bei solchen Räumen, in denen die Entstehung einer explosionsfähigen Atmosphäre möglich ist, müssen die Zündquellen, das heißt die Entstehung von Reib- und Schlagfunken, Reibungswärme und elektrische Auf tadung vermieden werden und mögliche Auswirkungen einer Explosion durch vorbeugende und konstruktive Maßnahmen berücksichtigt werden. Explosionsgeschützte Blockmotoren, insbesondere Normmotoren in Flanschausführung, lassen an den Schnittstellen, insbesondere Flansch und Welle, nur einen bestimmten Wärmeeintrag in den Motor zu, derart, dass die maximal zulässigen Temperaturen des Motors nicht überschritten werden. Such pump assemblies are widely used and find their application in almost all areas of industry. Machines of the present type are also used in potentially explosive areas. For the various production and conveying systems, especially in the field of chemistry, there are special regulations in connection with explosion protection. In such systems find on the one hand work machines, such as pumps or turbines, as non-electrical equipment, and on the other hand, power engines, such as drive motors, as electrical equipment, use. For electrical devices have long been proven safety standards. These standards specify which structural measures have to be taken in order to be able to use an electrical device in the various potentially explosive atmospheres. In such rooms, in which the emergence of a Explosive atmosphere is possible, the sources of ignition, that is the formation of friction and impact sparks, frictional heat and electrical charging must be avoided and possible effects of an explosion by preventive and constructive measures are taken into account. Explosion-proof block motors, in particular standard motors in flange design, allow only a certain heat input into the motor at the interfaces, in particular flange and shaft, such that the maximum permissible temperatures of the motor are not exceeded.
Inzwischen ist bekannt, dass bei Magnetkupplungspumpenanordnungen der Haupt- Wärmeeintrag in den Antriebsmotor durch dessen Antriebswelle erfolgt, da der Außen- magnetträger der Magnetkupplung sowohl der Medientemperatur, wie auch der Temperaturerhöhung durch die Wirbelstromverluste ausgesetzt ist. Durch die schlechte Wärmeabfuhr des Außenmagnetträgers infolge des ebenfalls erwärmten Pumpengehäuses wird die Wärmeenergie zu einem großen Teil direkt in die Antriebswelle eingetragen. It is now known that in magnetic coupling pump arrangements the main heat input into the drive motor takes place through its drive shaft, since the outer magnet carrier of the magnetic coupling is exposed both to the temperature of the medium and to the temperature increase due to the eddy current losses. Due to the poor heat dissipation of the outer magnetic carrier due to the likewise heated pump housing, the heat energy is entered to a large extent directly into the drive shaft.
Bei der DE 298 14 113 U1 wird dieses Problem umgangen, indem der als Treiber bezeichnete Außenrotor und der Antriebsmotor über ein Antriebsmittel aus schlecht wärmeleitendem Material in Antriebsverbindung stehen. Nachteilig ist hierbei die kostenintensive Ausführungsform mit einem zwischengelagerten Außenrotor. Denn neben zu- sätzlich erforderlichen Bauteilen sind neben dem Motorwälzlager auch die den Außenrotor lagernden Rillenkugellager zu warten. Außerdem ist die Wärmesperrefunktion nur auf die Schnittstelle zum Motorwellenstumpf hin existent. Da jedoch die Wärme direkt in den Innenring der Rillenkugellager eingetragen wird, kommt es zur Aufweitung des Innenrings und damit zur Verspannung des Lagers und folglich zur Standzeitreduzierung. Bei einer mit Kühlmittel agierenden Ausführungsform läuft der Außenrotor im Kühlmittel, wodurch erhebliche Reibungsverluste entstehen, welche den Wirkungsgrad der Pumpe deutlich reduzieren. In DE 298 14 113 U1, this problem is circumvented by the external rotor designated as the driver and the drive motor being in drive connection via a drive means made of poorly heat-conducting material. The disadvantage here is the cost-intensive embodiment with an intermediate outer rotor. Because apart from additionally required components, the deep groove ball bearings supporting the outer rotor are to be maintained in addition to the motor roller bearing. In addition, the thermal lock function is only existent on the interface to the motor shaft stub. However, since the heat is entered directly into the inner ring of the deep groove ball bearings, there is a widening of the inner ring and thus to the stress of the bearing and thus to reduce the service life. In an embodiment acting with coolant, the outer rotor runs in the coolant, resulting in considerable friction losses, which significantly reduce the efficiency of the pump.
Die Aufgabe der Erfindung besteht darin, eine Pumpenanordnung bereitzustellen, die bei gesteigerter Temperatur des zu fördernden Mediums, bei gleichzeitiger Einhaltung des Explosionsschutzes des Antriebsmotors, eine Verringerung des axialen und radialen Bauraumes und Vereinfachung der Montage ermöglicht. Die Aufgabe der Erfindung wird dadurch gelöst, dass der Außenrotor zwischen der Nabe und dem ersten Trägerelement einen hohlzylinderartigen Abschnitt aufweist. Dadurch, dass die Nabe nicht direkt an dem ersten Trägerelement angeordnet ist, sondern dem hohlzylinderartigen Abschnitt nachgeordnet an die Antriebswelle angeschlossen wird, wird der Wärmeeintrag von dem Außenmagnetträger in die Antriebswelle und somit in den Antriebsmotor reduziert. Nach einer Ausgestaltung der Erfindung sind der hohlzylinderartige Abschnitt und die Nabe gegenüber dem ersten Trägerelement dünnwandig ausgebildet. Der hohlzylinderartige Abschnitt und die Nabe weisen jeweils eine Wand mit einer bestimmten Wandstärke auf, wobei die Wandstärke der Wand des hohlzylinderartigen Abschnitts und die Wandstärke der Wand der Nabe kleiner als der Radius der Antriebswelle ausgebildet und so gewählt sind, dass in jedem Fall eine sichere Torsions- und Biegewechselfestigkeit gewährleistet ist. Dies führt zu einer weiteren Reduzierung des Wärmeeintrags von dem Außenmagnetträger in die Antriebswelle des Antriebsmotors. The object of the invention is to provide a pump assembly which allows for increased temperature of the medium to be delivered, while maintaining the explosion protection of the drive motor, a reduction of the axial and radial space and ease of assembly. The object of the invention is achieved in that the outer rotor between the hub and the first support member has a hollow cylindrical portion. Characterized in that the hub is not disposed directly on the first support member, but the hollow cylinder-like portion is connected downstream of the drive shaft, the heat input is reduced by the outer magnet carrier in the drive shaft and thus in the drive motor. According to one embodiment of the invention, the hollow-cylindrical portion and the hub with respect to the first support member are formed thin-walled. The hollow cylindrical portion and the hub each have a wall with a certain wall thickness, wherein the wall thickness of the wall of the hollow cylindrical portion and the wall thickness of the wall of the hub is smaller than the radius of the drive shaft and chosen so that in each case a safe torsion - And bending fatigue strength is guaranteed. This leads to a further reduction of the heat input from the outer magnet carrier in the drive shaft of the drive motor.
Eine vorteilhafte Ausgestaltung sieht vor, dass die axiale Fixierung des Außenmagnet- trägers an der Antriebswelle durch ein Befestigungselement erfolgt. An advantageous embodiment provides that the axial fixing of the outer magnetic carrier takes place on the drive shaft by a fastening element.
Dabei weist idealerweise das Befestigungselement an einem Ende ein erstes Außengewinde und an dem dem ersten Außengewinde gegenüberliegenden Ende ein zweites Außengewinde auf, wobei sich zwischen dem ersten Außengewinde und dem zweiten Außengewinde ein Distanzhalteabschnitt befindet, dessen Außendurchmesser größer ist als die Außendurchmesser des ersten Außengewindes und des zweiten Außengewindes. In this case, ideally, the fastening element has a first external thread at one end and a second external thread at the end opposite the first external thread, wherein a spacer holding section is located between the first external thread and the second external thread whose outer diameter is greater than the outer diameter of the first external thread and second external thread.
Als besonders vorteilhaft hat sich eine Ausgestaltung erwiesen, wonach der Distanzhal- teabschnitt an der dem ersten Außengewinde nahen Seite einen Bund mit vergrößertem Außendurchmesser aufweist, wodurch das Befestigungselement exakt axial positioniert und unkompliziert befestigt werden kann. Alternativ kann der Distanzhalteabschnitt an der dem ersten Außengewinde nahen Seite konisch auslaufen. An embodiment which has proven to be particularly advantageous is that the spacer section on the side close to the first external thread has a collar with an enlarged outside diameter, as a result of which the fastening element can be positioned exactly axially and fastened in an uncomplicated manner. Alternatively, the spacer portion on the side close to the first external thread may taper conically.
Zweckmäßigerweise ist in der Nabe eine radiale Gewindebohrung ausgebildet, in die ein Schraubelement eingeschraubt ist. Somit wird während des Stillstandes der Pumpenanordnung die Nabe in Anlage an die Stelle der Antriebswelle bewegt, an der die Nabe während des Betriebs in Anlage gerät. Dadurch wird eine hohe Rundlaufgenauigkeit erreicht. Appropriately, a radial threaded bore is formed in the hub into which a screw is screwed. Thus, during standstill of the pump assembly, the hub is moved into abutment with the location of the drive shaft where the hub engages during operation. As a result, a high concentricity is achieved.
Ausführungsbeispiele der Erfindung sind in den Zeichnungen dargestellt und werden im Folgenden näher beschrieben. Es zeigt die Embodiments of the invention are illustrated in the drawings and will be described in more detail below. It shows the
Fig. 1 den Längsschnitt durch eine Magnetkupplungspumpenanordnung mit einem erfindungsgemäßen Außenrotor, die Fig. 1 shows a longitudinal section through a magnetic coupling pump assembly with an external rotor according to the invention, the
Fig. 2 einen der Fig. 1 entsprechenden Außenrotor in vergrößerter Darstellung und die Fig. 3 einen Schnitt entlang der Linie Ill-Ill aus Fig. 2. FIG. 2 is an enlarged view of an outer rotor corresponding to FIG. 1, and FIG. 3 is a section along the line III-III of FIG. 2.
Die Fig. 1 zeigt eine Pumpenanordnung 1 in Form einer Magnetkupplungspumpenanordnung mit einem Pumpenteil und einem elektrischen Teil. Der Pumpenteil der Pumpenanordnung 1 weist ein mehrteiliges Pumpengehäuse 2 einer Kreiselpumpe auf, das ein als Spiralgehäuse gestaltetes Hydraulikgehäuse 3, einen Gehäusedeckel 4, eine Lagerträgerlaterne 5 und ein Verbindungselement 6 umfasst. FIG. 1 shows a pump arrangement 1 in the form of a magnetic coupling pump arrangement with a pump part and an electrical part. The pump part of the pump arrangement 1 has a multipart pump housing 2 of a centrifugal pump, which comprises a hydraulic housing 3 designed as a spiral housing, a housing cover 4, a bearing support lantern 5 and a connecting element 6.
Das Hydraulikgehäuse 3 weist eine Einlassöffnung 7 zum Ansaugen eines Fördermediums und eine Auslassöffnung 8 zum Ausstoßen des Fördermediums auf. Der Gehäuse- deckel 4 ist an der der Einlassöffnung 7 gegenüberliegenden Seite des Hydraulikgehäuses 3 angeordnet. An der dem Hydraulikgehäuse 3 abgewandten Seite des The hydraulic housing 3 has an inlet opening 7 for sucking in a conveyed medium and an outlet opening 8 for ejecting the conveyed medium. The housing cover 4 is arranged on the side of the hydraulic housing 3 opposite the inlet opening 7. On the side facing away from the hydraulic housing 3 of the
Gehäusedeckels 4 ist die Lagerträgerlaterne 5 befestigt. Das Verbindungselement 6 ist an der dem Gehäusedeckel 4 gegenüberliegenden Seite der Lagerträgerlaterne 5 angebracht. An das Verbindungselement 6 ist an der der Lagerträgerlaterne 5 entgegengesetzten Seite ein den elektrischen Teil bildenden Antriebsmotor 9 angeordnet. 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 Verbindungselement 6 begrenzten fnnenraum 11. Der Spalttopf 10 dichtet eine von ihm umschlossene Kammer 12 hermetisch gegenüber dem Innenraum 11 ab. Housing cover 4, the bearing bracket lantern 5 is attached. The connecting element 6 is attached to the housing cover 4 opposite side of the bearing bracket lantern 5. To the connecting element 6, a drive motor 9 forming the electrical part is arranged on the opposite side of the bearing support lantern 5. A containment shell 10 is fastened to the side of the housing cover 4 facing away from the hydraulic housing 3 and extends at least partially through an inner space 11 bounded by the pump housing 2, in particular by the housing cover 4, by the bearing support lantern 5 and by the connecting element 6. The containment shell 10 seals one of enclosed chamber 12 hermetically against the interior 11 from.
Eine um eine Drehachse A drehbare Laufradwelle 13 erstreckt sich von einer mittels des Hydraulikgehäuses 3 und des Gehäusedeckels 4 begrenzten Strömungskammer 14 durch eine in dem Gehäusedeckel 4 vorgesehene Öffnung 15 in die Kammer 12. An einem innerhalb der Strömungskammer 14 liegenden Wellenende der Laufrad welle 13 ist ein Laufrad 16 befestigt, am gegenüberliegenden Wellenende, das zwei Wellenabschnitte 13a, 13b mit sich jeweils vergrößernden Durchmessern aufweist, ist ein innerhalb der Kammer 12 angeordneter Innenrotor 17 angeordnet. Der Innenrotor 17 ist mit mehreren Magneten 18 bestückt, die an der dem Spaittopf 10 zugewandten Seite des Innenrotors 17 angeordnet sind. An about a rotational axis A rotatable impeller shaft 13 extends from a limited by means of the hydraulic housing 3 and the housing cover 4 flow chamber 14 through an opening provided in the housing cover 4 opening 15 into the chamber 12. At a lying within the flow chamber 14 shaft end of the impeller shaft 13 an impeller 16 fixed at the opposite shaft end, which has two shaft portions 13a, 13b each with increasing diameters, an arranged inside the chamber 12 inner rotor 17 is arranged. The inner rotor 17 is equipped with a plurality of magnets 18, which are arranged on the side of the inner rotor 17 facing the spit pot 10.
Zwischen Laufrad 16 und Innenrotor 17 ist eine mit der um die Drehachse A drehbar antreibbaren Laufradweife 13 in Wirkverbindung stehende Lageranordnung 19 angeordnet. Between the impeller 16 and the inner rotor 17, a bearing assembly 19 operatively connected to the impeller wheel 13 rotatably driven about the axis of rotation A is arranged.
Der Antriebsmotor 9 umfasst eine Antriebswelle 20. Die um die Drehachse A antreibbare Antriebswelle 20 ist im Wesentlichen koaxial zur Laufradwelle 13 angeordnet. Die Antriebswelle 20 erstreckt sich in das Verbindungselement 6 und ggf. wenigstens teilweise in die Lagerträgerlaterne 5. Am freien Ende der Antriebswelle 20 ist ein mehrere Magnete 21 tragender Außenrotor 22 angeordnet. Die Magnete 21 sind an der dem Spalttopf 10 zugewandten Seite des Außenrotors 22 angeordnet. Der Außenrotor 22 erstreckt sich zumindest teilweise über den Spalttopf 10 und wirkt mit dem Innenrotor 17 zusammen, derart, dass der rotierende Außenrotor 22 mitteis magnetischer Kräfte den Innenrotor 17 und somit die Laufradwelle 13 und das Laufrad 16 ebenfalls in eine Rotationsbewegung versetzt. Der in der Fig. 2 vergrößert dargestellte Außenrotor 22 umfasst eine Nabe 23 mit einer Außenmantelfläche 24, einen an der dem Antriebsmotor 9 abgewandten Seite der Nabe 23 ausgebildeten hohlzylinderartigen Abschnitt 25 mit einer durch eine Wandung 26 begrenzten Zelle 27. Der Außenrotor 22 umfasst ferner ein an der dem Spalttopf 10 zugewandten Seite des hohlzylinderartigen Abschnitts 25 ausgebildetes oder angeordne- tes flanschartiges erstes Trägerelement 28 und ein an dem ersten Trägerelement 28 ausgebildetes oder angeordnetes hohlzylinderartiges zweites Trägerelement 29, das zumindest teilweise den Spalttopf 10 umgibt und an dem die Magnete 21 angeordnet sind. Erstes und zweites Trägerelement 28, 29 sind als zwei miteinander verbindbare Teile dargestellt, können aber auch als ein Teil hergestellt werden. The drive motor 9 comprises a drive shaft 20. The drive shaft 20 which can be driven about the axis of rotation A is arranged essentially coaxially to the rotor shaft 13. The drive shaft 20 extends into the connecting element 6 and possibly at least partially into the bearing support lantern 5. At the free end of the drive shaft 20, a plurality of magnets 21 supporting outer rotor 22 is arranged. The magnets 21 are arranged on the side of the outer rotor 22 facing the containment shell 10. The outer rotor 22 extends at least partially over the containment shell 10 and interacts with the inner rotor 17 together, such that the rotating outer rotor 22 mitteis magnetic forces the inner rotor 17 and thus the impeller shaft 13 and the impeller 16 also set in a rotational movement. The outer rotor 22 shown enlarged in FIG. 2 comprises a hub 23 with an outer circumferential surface 24, a hollow cylindrical portion 25 formed on the side of the hub 23 facing away from the drive motor 9 with a cell 27 bounded by a wall 26. The outer rotor 22 further comprises a at the side facing the gap pot 10 side of the hollow cylinder-like portion 25 formed or angeordne- tes first support member 28 and a formed on the first support member 28 hollow cylinder-like second support member 29 which at least partially surrounds the can 10 and on which the magnets 21 are arranged , First and second support members 28, 29 are shown as two interconnectable parts, but may also be made as one part.
Der hohlzyiinderartige Abschnitt 25 weist eine Wand 25a mit einer Wandstärke S1 und die Nabe 23 eine Wand 23a mit einer Wandstärke S2 auf. Der hohlzyiinderartige Abschnitt 25 und die Nabe 23 sind gegenüber dem ersten Trägerelement 28 dünnwandig ausgebildet. Die Wandstärken S1 , S2 sind wesentlich kleiner, als die Dicke d1 des ers- ten Trägerelements 28. Die Wandstärke S1 der Wand 25a des hohlzylinderartigen Abschnitts 25 und die Wandstärke S2 der Wand 23a der Nabe 23 sind so gewählt, dass in jedem Fall eine sichere Torsions- und Biegewechselfestigkeit gewährleistet ist. Die Wandstärken S1 , S2 sind zudem kleiner als der Radius r der Antriebswelle 20 ausgebildet. Vorzugsweise ist die Wandstärke S1 der Wand 25a kleiner als die Wandstärke S2 der Wand 23a ausgebildet. The hollow-cyan-like section 25 has a wall 25a with a wall thickness S1 and the hub 23 has a wall 23a with a wall thickness S2. The hollow-cylinder-like portion 25 and the hub 23 are formed thin-walled with respect to the first support member 28. The wall thicknesses S1, S2 are substantially smaller than the thickness d1 of the first carrier element 28. The wall thickness S1 of the wall 25a of the hollow cylinder-like portion 25 and the wall thickness S2 of the wall 23a of the hub 23 are chosen such that in each case a safe Torsions- and bending fatigue strength is ensured. The wall thicknesses S1, S2 are also smaller than the radius r of the drive shaft 20. Preferably, the wall thickness S1 of the wall 25a is smaller than the wall thickness S2 of the wall 23a.
Durch die Nabe 23 erstreckt sich eine Durchgangsbohrung 30 bis in die Zelle 27 des zwischen der Nabe 23 und dem ersten Trägerelement 28 angeordneten hohlzylinderartigen Abschnitts 25 und bildet eine Nabeninnenfläche 31. In der Nabeninnenfläche 31 ist eine sich parallel zur Drehachse A erstreckende Axialnut 32 vorgesehen. In der Antriebswelle 20 ist eine zur Axialnut 32 hin ausgerichtete Passfedernnut 33 ausgebildet, in die zur Übertragung des Motordrehmoments auf die Nabe 23 des Außenrotors 22 eine Passfeder 34 eingesetzt ist. Die axiale Fixierung des Außenrotors 22 an der Antriebswelle 20 erfolgt durch ein Befestigungselement 35. Through the hub 23, a through hole 30 extends into the cell 27 of the arranged between the hub 23 and the first support member 28 hollow cylindrical portion 25 and forms a hub inner surface 31. In the hub inner surface 31 is a parallel to the axis of rotation A extending axial groove 32 is provided. In the drive shaft 20, a keyway 33 oriented toward the axial groove 32 is formed, into which the motor torque is transmitted to the hub 23 of the outer rotor 22 a feather key 34 is inserted. The axial fixing of the outer rotor 22 to the drive shaft 20 is effected by a fastening element 35.
Das Befestigungselement 35 weist an einem Ende ein in eine an der Stirnseite der An- triebswelle 20 koaxial mit der Drehachse A ausgebildete Gewindebohrung 36 einschraubbares erstes Außengewinde 37 und an dem dem ersten Außengewinde 37 gegenüberliegenden Ende ein zweites Außengewinde 38 auf. Zwischen dem ersten Außengewinde 37 und dem zweiten Außengewinde 38 ist ein Distanzhalteabschnitt 39 ausgebildet, dessen Außendurchmesser größer ist als die Außendurchmesser des ers- ten Außengewindes 37 und des zweiten Außengewindes 38. The fastening element 35 has at one end a first external thread 37 which can be screwed into a threaded bore 36 formed coaxially with the rotation axis A on the end face of the drive shaft 20, and a second external thread 38 at the end opposite the first external thread 37. Between the first external thread 37 and the second external thread 38, a spacer holding portion 39 is formed, the outer diameter of which is greater than the outer diameter of the first external thread 37 and the second external thread 38.
Das Befestigungselement 35 wird mit dem ersten Außengewinde 37 in die Gewinde- bohrung 36 eingeschraubt, bis der Distanzhalteabschnitt 39 in Anlage an die Stirnseite der Antriebswelle 20 gelangt. Bei der in den Fig. 1 und 2 gezeigten Ausführungsform, weist der Distanzhalteabschnitt 39 an der dem ersten Außengewinde 37 nahen Seite einen Bund 40 mit vergrößertem Außendurchmesser auf, der an der Antriebswelle 20 anliegt. Der Bund 40 ist vorzugsweise als Sechskant aufgeführt oder weist zumindest zwei Schlüsselflächen auf. Alternativ kann der Distanzhalteabschnitt 39 an der dem ersten Außengewinde 37 nahen Seite konisch auslaufen und in Anlage mit dem konischen Eingangsbereich der Gewindebohrung 36 gelangen. The fastening element 35 is screwed into the threaded bore 36 with the first external thread 37 until the spacer holding section 39 comes into contact with the end face of the drive shaft 20. In the embodiment shown in Figs. 1 and 2, the spacer holding portion 39 on the first external thread 37 side near a collar 40 with an enlarged outer diameter, which rests against the drive shaft 20. The collar 40 is preferably listed as a hexagon or has at least two key surfaces. Alternatively, the spacer holding section 39 on the side close to the first external thread 37 may taper conically and come into abutment with the conical inlet region of the threaded bore 36.
Das zweite Außengewinde 38 erstreckt sich durch eine Öffnung 41 in der Wandung 26, wobei sich der Distanzhalteabschnitt 39 des Befestigungselements 35 in Anlage an der Wandung 26 befindet. Mit einer auf das zweite Außengewinde 38 aufgeschraubten Schraubenmutter 42 erfolgt die axiale Fixierung des Außenrotors 22 an der Antriebswelle 20. Der Außenrotor 22 ist auf diese Weise axial exakt positionierbar und auf einfache Weise befestigbar. Zusätzlich erstreckt sich eine Durchgangsbohrung 43 von einer Stirnseite des Befestigungselements 35 zur anderen, um das die Wärme vom Außenrotor 22 in die Antriebswelle 20 übertragende Material so gering wie möglich zu halten. Alternativ kann anstelle der Durchgangsbohrung 43 eine Sacklochbohrung vorgesehen werden, die sich entweder von der dem ersten Außengewinde 37 nahen Stirnseite bis nahe an oder in den Distanzhalteabschnttt 39 oder von der dem zweiten Außengewinde 38 nahen Stirnseite bis zum Bund 40 oder darüber hinaus erstreckt. The second external thread 38 extends through an opening 41 in the wall 26, wherein the spacer holding portion 39 of the fastening element 35 is in contact with the wall 26. With a screwed onto the second external thread 38 nut 42, the axial fixing of the outer rotor 22 takes place on the drive shaft 20. The outer rotor 22 is in this way axially accurately positioned and fastened in a simple manner. In addition, a through hole 43 extends from one end face of the fastener 35 to the other to keep the heat transferring the heat from the outer rotor 22 into the drive shaft 20 as small as possible. Alternatively, instead of the through hole 43, a blind hole can be provided, which extends either from the first external thread 37 near end face extends close to or in the Distanzhalteabschnttt 39 or from the second external thread 38 near the end face to the collar 40 or beyond.
Die Fig. 3 zeigt, dass in der Nabe 23 eine radiale Gewindebohrung 44 ausgebildet ist, in die ein Schraubelement 45, insbesondere Madenschraube, eingeschraubt ist. Das der Antriebswelle 20 zugewandte Ende des Schraubelements 45 ist vorzugsweise kegel- stumpfartig ausgebildet. Die Gewindebohrung 44 ist immer in Dehrichtung der angetriebenen Antriebswelle 20, die hier durch den Pfeil M angegeben ist, in einem Winkel α von etwa 35° bis etwa 55° und vorzugsweise in einem Winkel α von 40° bis 50° und bevorzugt in einen Winkel α von etwa 45° zur Axialnut 32 angeordnet. Bei Bedarf befinden sich entlang ihrer axialen Erstreckung weitere, nicht dargestellte, Gewindebohrungen 44 in der Nabe 23. 3 shows that a radial threaded bore 44 is formed in the hub 23, into which a screw element 45, in particular grub screw, is screwed. The drive shaft 20 facing the end of the screw 45 is preferably formed like a truncated cone. The threaded bore 44 is always in Dehrichtung the driven drive shaft 20, which is indicated here by the arrow M, at an angle α of about 35 ° to about 55 ° and preferably at an angle α of 40 ° to 50 ° and preferably at an angle α of about 45 ° to the axial groove 32 is arranged. If necessary, there are further, not shown, threaded holes 44 in the hub 23 along its axial extent.
Bezugszeichenliste LIST OF REFERENCE NUMBERS
1 Pumpenanordnung 25a Wand 1 pump assembly 25a wall
2 Pumpengehäuse 26 Wandung  2 pump housing 26 wall
3 Hydraulikgehäuse 27 Zelle  3 hydraulic housing 27 cell
4 Gehäusedeckel 28 erstes Trägerelement  4 housing cover 28 first carrier element
5 Lagerträgerlaterne 29 zweites Trägerelement 5 bearing support lantern 29 second support element
6 Verbindungselement 30 Durchgangsbohrung 6 connecting element 30 through-hole
7 Einlassöffnung 31 Nabeninnenfläche  7 inlet opening 31 hub inner surface
8 Auslassöffnung 32 Axialnut  8 outlet opening 32 axial groove
9 Antriebsmotor 33 Passfedernut  9 Drive motor 33 Keyway
10 Spalttopf 34 Passfeder  10 split pan 34 feather key
11 Innenraum 35 Befestigungselement  11 Interior 35 Fastening element
12 Kammer 36 Gewindebohrung  12 chamber 36 threaded hole
13 Laufradwelle 37 erstes Außengewinde  13 impeller shaft 37 first external thread
13a Wellenabschnitt 38 zweites Außengewinde 13b Wellenabschnitt 39 Distanzhalteabschnitt  13a shaft portion 38 second external thread 13b shaft portion 39 spacer holding portion
14 Strömungskammer 40 Bund  14 flow chamber 40 collar
15 Öffnung 41 Öffnung  15 opening 41 opening
16 Laufrad 42 Schraubenmutter  16 impeller 42 nut
17 Innenrotor 43 Durchgangsbohrung  17 Inner rotor 43 Through hole
18 Magnet 44 Gewindebohrung  18 magnet 44 threaded hole
19 Lageranordnung 45 Schraubelement  19 Bearing assembly 45 screw
20 Antriebswelle  20 drive shaft
21 Magnet A Drehachse  21 Magnet A rotation axis
22 Außenrotor 51 Wandstärke hohfzyl. Abschnitt 22 outer rotor 51 Wall thickness hohfzyl. section
23 Nabe 52 Wandstärke Nabe 23 hub 52 wall thickness hub
23a Wand r Radius Antriebswelle  23a wall r radius drive shaft
24 Außenmantelfläche  24 outer circumferential surface
25 hohizyltnderartigen Abschnitt  25 hohizyltnderartigen section

Claims

Patentansprüche Pumpenanordnung Claims Pump arrangement
1. Pumpenanordnung, insbesondere Magnetkupplungspumpenanordnung, mit einem von einem Pumpengehäuse der Pumpenanordnung gebildeten Innenraum, einem Spalttopf, der eine von ihm umschlossene Kammer hermetisch gegenüber dem vom Pumpengehäuse gebildeten Innenraum abdichtet, einer um eine Drehachse drehbar antreibbaren Laufradwelle, einem an einem Ende der Laufradwelle angeordneten Laufrad, einem an dem anderen Ende der Laufradwelle angeordneten Innenroior, einem Antriebsmotor, einer von dem Antriebsmotor drehbar um die Drehachse antreibbare Antriebswelle und einem auf der Antriebswelle angeordneten, mit dem Innenrotor zusammenwirkenden Außenrotor, wobei der Außenrotor eine Nabe sowie ein erstes Trägerelement aufweist, dadurch gekennzeichnet, dass der Außenrotor (22) zwischen der Nabe (23) und dem ersten Trägerelement (28) einen hohlzylinderartigen Abschnitt (25) aufweist. 1. Pump arrangement, in particular magnetic coupling pump arrangement, with a housing formed by a pump housing of the pump assembly, a containment shell which hermetically seals a chamber enclosed by him against the inner space formed by the pump housing, a rotatably driven about an axis of rotation impeller shaft, one arranged at one end of the impeller shaft Impeller, arranged at the other end of the impeller shaft Innenroior, a drive motor, rotatably driven by the drive motor about the axis of rotation drive shaft and arranged on the drive shaft, cooperating with the inner rotor outer rotor, wherein the outer rotor has a hub and a first support member, characterized characterized in that the outer rotor (22) has a hollow-cylindrical section (25) between the hub (23) and the first carrier element (28).
2. Pumpenanordnung nach Anspruch 1, dadurch gekennzeichnet, dass der hohl- zylinderartige Abschnitt (25) und die Nabe (23) gegenüber dem ersten Trägerelement (28) dünnwandig ausgebildet sind. 2. Pump arrangement according to claim 1, characterized in that the hollow cylinder-like portion (25) and the hub (23) opposite the first support member (28) are formed thin-walled.
3. Pumpenanordnung nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass die axiale Fixierung des Außenrotors (22) an der Antriebswelle (20) durch ein Be- festigungselement (35) erfolgt. 3. Pump arrangement according to claim 1 or 2, characterized in that the axial fixing of the outer rotor (22) on the drive shaft (20) by a fastening element (35).
4. Pumpenanordnung nach Anspruch 3, dadurch gekennzeichnet, dass das Befestigungselement (35) an einem Ende ein erstes Außengewinde (37) und an dem dem ersten Außengewinde (37) gegenüberliegenden Ende ein zweites Außengewinde (38) aufweist, wobei sich zwischen dem ersten Außengewinde (37) und dem zweiten Außengewinde (38) ein Distanzhalteabschnitt (39) befindet, dessen Außendurchmesser größer ist als die Außendurchmesser des ersten Außengewindes (37) und des zweiten Außengewindes (38). 4. Pump arrangement according to claim 3, characterized in that the fastening element (35) at one end a first external thread (37) and at the first external thread (37) opposite end a second external thread (38), wherein between the first external thread (37) and the second external thread (38) is a spacer holding portion (39) whose outer diameter is greater than the outer diameter of the first external thread (37) and the second external thread (38).
5. Pumpenanordnung nach Anspruch 4, dadurch gekennzeichnet, dass der Distanzhalteabschnitt (39) an der dem ersten Außengewinde (37) nahen Seite einen Bund (40) mit vergrößertem Außendurchmesser aufweist. 5. Pump arrangement according to claim 4, characterized in that the spacer holding portion (39) on the first external thread (37) near side a collar (40) having an enlarged outer diameter.
6. Pumpenanordnung nach Anspruch 4, dadurch gekennzeichnet, dass der Distanzhalteabschnitt (39) an der dem ersten Außengewinde (37) nahen Seite konisch ausläuft. 6. Pump arrangement according to claim 4, characterized in that the spacer holding portion (39) at the first external thread (37) near side tapers conically.
7. Pumpenanordnung nach einem der Ansprüche 1 bis 6, dadurch gekennzeichnet, dass in der Nabe (23) eine radiale Gewindebohrung (44) ausgebildet ist, in die ein Schraubelement (45) eingeschraubt ist. 7. Pump arrangement according to one of claims 1 to 6, characterized in that in the hub (23) has a radial threaded bore (44) is formed, into which a screw member (45) is screwed.
EP14719796.6A 2013-05-08 2014-04-29 Magnetic drive pump assembly Active EP2994641B1 (en)

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DE102013208536.2A DE102013208536A1 (en) 2013-05-08 2013-05-08 pump assembly
PCT/EP2014/058701 WO2014180711A1 (en) 2013-05-08 2014-04-29 Pump arrangement

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EP2994641A1 true EP2994641A1 (en) 2016-03-16
EP2994641B1 EP2994641B1 (en) 2017-08-16

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US (1) US9869316B2 (en)
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JP (1) JP6423864B2 (en)
KR (1) KR102088479B1 (en)
CN (1) CN105408632B (en)
AU (1) AU2014264828B2 (en)
BR (1) BR112015028023B1 (en)
DE (1) DE102013208536A1 (en)
DK (1) DK2994641T3 (en)
ES (1) ES2642339T3 (en)
HU (1) HUE034645T2 (en)
MX (1) MX364925B (en)
RU (1) RU2674296C2 (en)
SG (1) SG11201508902VA (en)
WO (1) WO2014180711A1 (en)
ZA (1) ZA201508072B (en)

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CN107191385B (en) * 2017-04-28 2023-12-01 合肥工业大学 Magnetic driving type water jet propulsion pump
DE102019002392A1 (en) * 2019-04-02 2020-10-08 KSB SE & Co. KGaA Thermal barrier
TWI694211B (en) * 2019-05-09 2020-05-21 大港泵浦廠興業有限公司 Pump
TWI692586B (en) * 2019-05-09 2020-05-01 大港泵浦廠興業有限公司 Pump
EP3757395B1 (en) * 2019-06-28 2023-06-07 Grundfos Holding A/S Electrical pump device with canned motor
CN113309707B (en) * 2021-04-12 2022-08-02 安徽南方化工泵业有限公司 High-compression-resistance type magnetic pump spacer bush and preparation method thereof

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Also Published As

Publication number Publication date
EP2994641B1 (en) 2017-08-16
MX364925B (en) 2019-05-10
SG11201508902VA (en) 2015-11-27
KR102088479B1 (en) 2020-03-13
BR112015028023B1 (en) 2022-03-15
WO2014180711A1 (en) 2014-11-13
KR20160006713A (en) 2016-01-19
DE102013208536A1 (en) 2014-11-13
JP2016518550A (en) 2016-06-23
HUE034645T2 (en) 2018-02-28
ES2642339T3 (en) 2017-11-16
CN105408632B (en) 2018-09-07
DK2994641T3 (en) 2017-11-27
RU2015148038A (en) 2017-06-14
RU2674296C2 (en) 2018-12-06
JP6423864B2 (en) 2018-11-14
MX2015015298A (en) 2016-02-18
AU2014264828A1 (en) 2015-11-12
AU2014264828B2 (en) 2017-05-25
BR112015028023A2 (en) 2017-07-25
CN105408632A (en) 2016-03-16
ZA201508072B (en) 2016-10-26
US20160084255A1 (en) 2016-03-24
US9869316B2 (en) 2018-01-16

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