EP2798224B2 - Groupe de pompe - Google Patents

Groupe de pompe Download PDF

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Publication number
EP2798224B2
EP2798224B2 EP12813319.6A EP12813319A EP2798224B2 EP 2798224 B2 EP2798224 B2 EP 2798224B2 EP 12813319 A EP12813319 A EP 12813319A EP 2798224 B2 EP2798224 B2 EP 2798224B2
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EP
European Patent Office
Prior art keywords
rotor
axial
impeller
pump assembly
rotor shaft
Prior art date
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Active
Application number
EP12813319.6A
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German (de)
English (en)
Other versions
EP2798224B1 (fr
EP2798224A1 (fr
Inventor
Thomas Blad
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Grundfos Holdings AS
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Grundfos Holdings AS
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Priority to EP12813319.6A priority Critical patent/EP2798224B2/fr
Publication of EP2798224A1 publication Critical patent/EP2798224A1/fr
Publication of EP2798224B1 publication Critical patent/EP2798224B1/fr
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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
    • 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
    • F04D13/0633—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
    • 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
    • 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
    • F04D29/041—Axial thrust balancing
    • 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
    • F04D29/041—Axial thrust balancing
    • F04D29/0413—Axial thrust balancing hydrostatic; hydrodynamic thrust 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
    • F04D29/00—Details, component parts, or accessories
    • F04D29/04—Shafts or bearings, or assemblies thereof
    • F04D29/042—Axially shiftable rotors
    • 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
    • F04D29/046—Bearings
    • F04D29/047—Bearings hydrostatic; hydrodynamic
    • F04D29/0473—Bearings hydrostatic; hydrodynamic for radial 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
    • F04D29/04—Shafts or bearings, or assemblies thereof
    • F04D29/046—Bearings
    • F04D29/049—Roller 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
    • F04D29/00—Details, component parts, or accessories
    • F04D29/08—Sealings
    • F04D29/16—Sealings between pressure and suction sides
    • F04D29/165—Sealings between pressure and suction sides especially adapted for liquid pumps
    • F04D29/167—Sealings between pressure and suction sides especially adapted for liquid pumps of a centrifugal flow wheel

Definitions

  • the invention relates to a pump unit with the features specified in the preamble of claim 1.
  • the electric drive motors are often designed as permanent magnet rotors, d. H. they have a permanent magnet rotor which rotates inside a stator. At least one pump impeller, which rotates in a pump housing, is connected to this permanent magnet rotor via a rotor shaft. During operation of the pump unit, an axial force acts on the shaft, which axial force is absorbed by a thrust bearing on the rotor shaft or the rotor.
  • These pump units are designed as wet-running pump units, d. H.
  • the rotor runs inside a canned or canned pot in the liquid to be pumped.
  • the bearings which store the rotor or the rotor shaft are usually lubricated by the liquid to be conveyed.
  • impurities contained in the liquid to be pumped can set the bearings, so that the motor can no longer start due to an insufficient starting torque.
  • the pump unit according to the invention has, as known pump units on an electric drive motor, which is preferably designed as a wet-running electric drive motor.
  • the electric drive motor has a stator and a rotor designed as a permanent magnet rotor.
  • the rotor is arranged inside a canned or canned pot, which separates the wet rotor space from the dry stator space in which the stator is arranged.
  • the pump unit has at least one impeller, which is connected via a rotor shaft to the rotor.
  • the impeller is preferably arranged in the interior of a pump housing, as defined in conventional centrifugal pump units, which defines the suction and pressure-side flow paths.
  • a thrust bearing is provided which receives the axial forces acting on the impeller and the rotor shaft during operation of the pump assembly. These are hydraulic axial forces which, in operation, are generally directed opposite to the inflow direction in which the liquid to be conveyed flows into the suction mouth of the impeller. The flow typically enters the impeller axially and radially out of the impeller.
  • the axial bearing is preferably arranged or formed on the rotor shaft or on the rotor.
  • at least one radial bearing is arranged on the rotor shaft. This radial bearing may be a separate component which is connected to the rotor shaft.
  • the inner bearing surface may be formed by the outer peripheral surface of the rotor shaft itself, which is on a fixed outer bearing surface in abutment.
  • the permanent magnet rotor and the stator are designed such that a magnetic axial force is generated between the rotor and the stator which acts in the direction of the axis of rotation of the rotor and which is directed in the opposite direction from the rotor to the stator of the inflow direction. Ie. Conversely, this additional axial force acts on the rotor in the direction of the inflow direction. Ie. this magnetic axial force counteracts the hydraulic axial force which occurs in normal operation and acts on the rotor.
  • the arrangement of permanent magnet rotor and stator is designed so that this magnetic axial force occurs even when the pump unit is not in operation, d. H. that the permanent magnetic force acts permanently, both during operation and during standstill of the drive motor.
  • this permanent magnetic axial force results from the arrangement of the permanent magnet rotor and the stator relative to each other. Ideally, therefore, no additional permanent magnetic or soft magnetic components are required. However, it is also conceivable, on the rotor and / or the stator an additional hard magnetic, d. H. Permanent magnetic or soft magnetic element or more such elements to be arranged, which generate the magnetic axial force or contribute to their generation.
  • the rotor shaft is slidably mounted with the rotor relative to the stator in the axial direction.
  • This arrangement makes it possible, by the additional magnetic axial force, to cause a displacement of the rotor shaft in the axial direction in certain operating conditions or in the idle state of the pump unit.
  • This makes it possible, as will be described below, at least partially disengage the bearings when the pump unit is not in operation, whereby a setting of the bearings can be avoided.
  • a seal of the rotor space as described below, can be achieved in the idle state to prevent ingress of impurities in the rotor space.
  • the rotor shaft is movable so that it can move axially in the inflow of the impeller in the idle state of the pump unit. Ie. at rest, the rotor shaft would move axially in the direction in which the liquid flows axially into the impeller due to the permanent magnetic force, since an opposing hydraulic force is absent. This is the direction which is directed opposite to the axial force acting in normal operation of the pump unit.
  • the hydraulic axial force is preferably greater than the magnetic force, so that due to the opposing action of the axial hydraulic force, the rotor shaft is again in the reverse direction, i. H. is moved against the inflow direction.
  • an axial force acting on the impeller and the rotor shaft during operation of the pump assembly is greater than the oppositely directed magnetic axial force.
  • the hydraulic axial force is greater than the oppositely directed magnetic axial force in the entire operating range or at least in the normal operating range of the pump unit. This ensures that the thrust bearing is held in a defined abutment on the rotor shaft or on the rotor by the hydraulic axial force during operation.
  • the hydraulic axial force falls away and it only acts the described permanent magnetic axial force, which then leads to a displacement of the rotor, wherein the at least one radial bearing at least partially disengaged.
  • the permanent magnetic axial force can then be reduced or canceled in the rest position. It is essential that the permanent magnetic axial force acts in operation of the pump unit against the hydraulic axial force, that the elimination of the hydraulic axial force, the magnetic axial force can cause a displacement of the rotor in the axial direction. Ie. According to the invention, the permanent magnetic axial force does not have to act on the rotor in all states of the pump unit, but only at least when the pump unit is switched off, in order then to displace the rotor shaft as desired in the axial direction. When restarting the pump unit can then be displaced by the occurring hydraulic axial force, the rotor shaft back into a position in which the at least radial thrust bearing is fully engaged.
  • the at least one radial bearing is configured in such a way that, when axial displacement of the rotor shaft in the inflow direction of the impeller caused by the magnetic axial force occurs, the opposing bearing surfaces of the radial bearing at least partially disengage.
  • the bearing surfaces of the radial bearing are opposite to each other and to each other. Due to the axial displacement is achieved that the bearing surfaces are moved axially relative to each other so that they overlap only in a smaller area, ie the overlap of the bearing surfaces is reduced, the bearing surfaces are partially disengaged.
  • the stator preferably surrounds the rotor circumferentially.
  • the permanent magnets in the rotor are usually magnetized in the radial direction or cause a radial magnetic field of the rotor.
  • the permanent magnetic magnetic field of the permanent magnet in the rotor interacts with the iron parts of the stator, whereby an additional axial force can be generated with a corresponding arrangement and design.
  • the additional magnetic axial force can be generated in that the rotor and the stator are designed and arranged such that at least during operation of the pump unit, the axial center of the rotor, d. H. the axial center of the magnetically active part of the rotor, in the direction opposite to the inflow direction, in which the liquid enters the impeller, is spaced from the axial center of the stator.
  • the rotor is arranged offset relative to the stator to the inlet opening or to the suction mouth. Due to the permanent magnetic magnetic field of the rotor, however, this endeavors to center in the interior of the iron core of the stator in the axial direction.
  • the axial offset thus generates a magnetic force which tends to pull the rotor into the centered position.
  • an additional axial force can be generated in the desired direction.
  • the at least one impeller is preferably fixed in the axial direction on the rotor shaft. This ensures that the magnetic axial force acting on the rotor, also acts on the impeller and beyond the impeller is fixed in the axial direction by the rotor.
  • the thrust bearing is designed such that its bearing surfaces when moving the rotor shaft in the inflow direction into the impeller out of engagement.
  • the at least one radial bearing is designed as a sliding bearing, of which a first bearing surface on the outer circumference of the rotor shaft and an opposite second bearing surface is formed in a fixed bearing ring.
  • the fixed bearing ring is preferably formed as a ceramic bearing ring.
  • the rotor shaft may preferably be formed as a ceramic shaft or at least preferably have ceramic bearing surfaces.
  • the diameter of the rotor shaft relative to the diameter of this bearing surface is reduced at least one side facing the impeller of a formed on the rotor shaft bearing surface of the radial bearing. This ensures that when the rotor shaft by the magnetic axial force in the direction away from the wheel, d. H. the inflow direction of the impeller is displaced, the diameter reduced surface of the rotor shaft enters the radial bearing or the bearing ring, so that in this area the bearing surface on the inner circumference of the bearing ring is no longer applied to the outer circumference of the rotor shaft. In this way, the bearing surfaces of the radial bearing at least partially disengaged, so that the friction when starting and the risk of setting the radial bearing is reduced.
  • two radial bearings are arranged on the rotor shaft, which are designed in the manner described above, wherein the two bearings are preferably located on opposite axial sides of the rotor.
  • a radial bearing is preferably located on the side facing away from the rotor of the rotor.
  • This radial bearing is preferably arranged in the vicinity of the bottom of a canned pot.
  • the second radial bearing is arranged on the side facing the impeller of the rotor and may be part of a combined radial thrust bearing, which is arranged between the rotor and impeller on the rotor shaft.
  • the opposing bearing surfaces of the radial bearing are dimensioned in their axial extent and arranged relative to each other such that they are disengaged by more than 50%, preferably more than 75% in the axial displacement of the rotor shaft.
  • the bearing surfaces are out of engagement, so that the friction is significantly reduced and the risk of settling of the bearing is minimized by contamination between the bearing surfaces.
  • the impeller is preferably sealed at its suction mouth via a suction seal against the pump housing.
  • the suction seal forms a stationary component on the pump housing.
  • the suction seal is arranged to the impeller such that upon an axial displacement of the rotor shaft in the inflow direction of the impeller, the suction seal and the impeller at least partially, preferably completely disengage.
  • the flowability of the pump assembly is improved at standstill, since so fluid can flow past the impeller through the pump housing and the impeller for this flow forms no or only a significantly reduced resistance.
  • this embodiment in which the suction of the impeller at standstill of the impeller out of engagement, in combination with the bearings, in which the bearing surfaces at least partially disengage at standstill used.
  • this arrangement of the suction seal on the impeller can also be realized independently of the corresponding design of the bearing.
  • the rotor shaft is displaceable by a degree which is smaller than or equal to an existing during operation of the pump assembly axial distance between the axial center of the rotor and the axial center of the stator. Ie. the axial mobility of the rotor shaft is limited and to a degree which is less than or equal to the axial displacement occurring between rotor and stator in operation. This ensures that a sufficient magnetic axial force always acts on the rotor shaft in order to be able to shift it by the desired amount.
  • an emergency bearing surface which faces a fixed thrust bearing surface, is formed on the at least one impeller on an axial side facing the rotor.
  • the hydraulic axial force acting on the impeller against the inflow direction can decrease so much that the thrust bearing receiving this force during operation is relieved. So it can happen that the bearing surfaces of this thrust bearing are no longer held in this operating condition in abutment.
  • the oppositely directed emergency bearing is provided.
  • the emergency is preferably used when the Rotor shaft is displaced in the manner described above by the magnetic force in the axial direction.
  • the emergency bearing serves as a stop which limits the movement of the rotor shaft in the axial direction. In the opposite direction, the movement is limited by the actual thrust bearing. Thus, the emergency bearing comes then also when starting the drive motor from the idle state, if the actual thrust bearing is not yet in abutment to effect.
  • the thrust bearing surface on which the emergency bearing surface comes to rest is preferably formed by an axial end face of a stationary bearing ring, a radial and / or thrust bearing of the rotor shaft.
  • this bearing ring is preferably a ceramic component whose front side preferably forms the actual axial bearing surface. This front side is the side facing away from the impeller and the rotor facing side of the bearing ring.
  • the radial bearing surface is formed by the inner peripheral surface of the bearing ring.
  • the bearing gap between the rotor shaft and the inner circumference of the bearing ring is simultaneously closed towards the pump chamber, in which the impeller is arranged, so that contaminants are prevented from entering the bearing gap can.
  • the impeller is arranged relative to the bearing ring such that the emergency bearing surface can be brought into contact with the fixed thrust bearing surface by the axial displacement of the rotor shaft.
  • the emergency bearing can be brought to bear against the bearing ring, so that in the idle state, when the pump unit is stationary, the bearing gap is closed by the emergency bearing surface.
  • the emergency bearing surface is further preferably formed by an axially projecting annular projection on the impeller.
  • the impeller is preferably made in one piece with this projection made of plastic.
  • the emergency bearing surface is preferably axially spaced from the fixed thrust bearing surface.
  • the normal thrust bearing is engaged to receive the axial hydraulic forces acting on the impeller and rotor.
  • the normal operating state is that in which such a hydraulic force acts opposite to the direction of inflow into the impeller.
  • the distance of the emergency bearing surface of the fixed thrust bearing surface is smaller than or equal to an existing in operation of the pump assembly axial distance between the axial center of the rotor and the axial center of the stator.
  • This arrangement ensures that when the rotor shaft is moved to bring the emergency bearing into and out of engagement with the thrust bearing surface, the offset is not greater than the offset between the rotor and the stator, so that there is always a magnetic axial force, which is the emergency bearing surface holds in abutment with the thrust bearing surface, as long as no oppositely acting hydraulic axial force leads to a displacement of the rotor shaft in the opposite direction and brings the emergency bearing surface of the thrust bearing surface disengaged.
  • At least one sealing element can be arranged between the rotor shaft or the impeller on the one side and a stationary bearing ring or a bearing holder on the other side, which can be brought into sealing engagement by the axial displacement of the rotor shaft. So can on the impeller z.
  • an annular sealing element may be arranged, which is also sealingly engageable with the end face of a fixed bearing ring to the plant.
  • the sealing element on the impeller could also be arranged or formed so that it is on the surface of a bearing or the bearing ring surrounding bearing support can come to the plant.
  • such a sealing element could also be arranged on the axial bearing surface of the bearing ring and the impeller come to rest there with a suitable sealing surface during axial movement of the rotor shaft. It would also be possible to arrange such an annular seal not on the impeller but on the rotor shaft so that it can come into contact, for example, with the stationary bearing ring. In all these arrangements, the seal can thus seal the bearing gap between the bearing ring and the rotor shaft in the idle state of the pump unit to prevent flow through the bearing and the ingress of contaminants.
  • this sealing of the bearing gap by axial displacement of the rotor shaft could also be realized independently of the configuration in which the bearings are at least partially disengaged by the axial displacement of the shaft. If the axial displacement of the rotor shaft is only used to bring the sealing element in and out of engagement, a much smaller axial displacement of the rotor shaft may be sufficient to effect this. This has the advantage that the rotor only has to be displaced axially relative to the stator by a small amount so that the magnetic efficiency is substantially not impaired.
  • the pump unit according to the invention has a pump housing 2, in which an impeller 4 is arranged.
  • the impeller 4 has an axially directed central suction mouth 6, through which the liquid to be conveyed enters the impeller 4.
  • the suction mouth 6 is located in the interior of the pump housing 2 against a flow channel, which opens into a suction nozzle 8.
  • a pressure port 10 is arranged on the pump housing 2, which is connected via a flow channel with the peripheral region of the impeller 4, which forms a spiral channel, in connection.
  • the impeller 4 is connected via a rotor shaft 12 with a permanent magnet rotor 14.
  • the rotor shaft 12 is preferably made of ceramic.
  • permanent magnets 16 are arranged, which generate a radially directed magnetic field of the rotor 14.
  • the permanent magnet rotor 14 is arranged in the interior of a split tube 18 or a canned pot 18.
  • the can 18 is surrounded by the stator 20.
  • the impeller 4 is rotationally fixed and fixed in the axial direction X fixed to the rotor shaft 12.
  • the rotor shaft 12 is slidably mounted in two ceramic bearing rings 22 and 24.
  • the bearing ring 22 is a pure radial bearing.
  • the bearing ring 24 simultaneously assumes the function of the thrust bearing.
  • the impeller 4 facing away from the axial end face of the bearing ring 24 is formed as a thrust bearing surface on which a connected to the rotor shaft 12 Axiallagering 26 comes to rest.
  • the thrust bearing 26 is fixed in the axial direction X on the rotor shaft 12.
  • the ceramic shaft 12 With its outer peripheral surfaces on the inner circumference of the bearing rings 22 and 24 slidably.
  • the rotor shaft 12 is movable in the axial direction X and is in the normal operation of the pump unit by the hydraulic axial force in the in Fig. 2 shown held state in which the rotor shaft 12 is moved counter to the inflow E so far that the thrust bearing ring on the axial side 28 of the bearing ring 24 slidably abuts.
  • the axial center MR of the rotor ie the magnetically active part of the rotor, is displaced from the axial center MS of the stator 20 or the iron part 30 by a dimension a in the axial direction.
  • the pump unit or the drive motor is designed so that this magnetic force in normal operation, ie preferably in most operating areas of the pump unit is smaller than the hydraulic force, so that the Axiallagerring 26 is held on the axial side 28 of the bearing ring 24 in abutment.
  • recesses 32 Adjacent to the regions of the rotor shaft 12, which form the bearing surfaces 22 and 24 cooperating radial bearing surfaces 34, recesses 32 are formed on the outer circumference of the rotor shaft, in the region of the outer diameter of the rotor shaft 12 is reduced.
  • the indentations 32 adjoin the side of the bearing surfaces 34 facing the impeller 4.
  • these recesses 32 are of reduced diameter in the bearing rings 22 and 24 and simultaneously enters a portion of the bearing surfaces 34 at the opposite axial end of the bearing rings 22 and 24 from. Ie. the bearing surfaces 34 are partially disengaged from the inner peripheral surfaces of the bearing rings 22 and 24, which form their radial bearing surfaces. In this way, the friction in the radial bearings 22 and 24 is reduced at rest and minimizes the risk of setting in the camps.
  • the impeller 4 is sealed at its suction mouth 6 via a suction seal 35 relative to the pump housing 2.
  • the suction seal 35 is fixed to the pump housing 2 and engages in the suction mouth 6 a.
  • the inner circumference of the suction mouth 6 thus overlaps the outer circumference of the suction seal 35, wherein the suction mouth 6 rotates relative to the suction seal 35.
  • the suction seal may be formed in a conventional manner as a collar-shaped sheet metal component.
  • the pump unit can be flowed through at a better standstill, since the flow through the gap between the suction seal 35 and the end face of the impeller 4 on the impeller can be done by the pump housing 2 to the discharge nozzle 10. This reduces the flow resistance at standstill.
  • the impeller 4 has on its end remote from the suction mouth 6 an annular projection 36 which faces the bearing ring 24.
  • the projection 36 is made in one piece with the impeller 4 made of plastic and forms an emergency bearing surface.
  • the rotor shaft 12 In operating states in which the hydraulic axial force is insufficient to hold the thrust bearing in abutment, ie to hold the thrust bearing ring 26 in abutment against the axial side 28 of the bearing ring 24, it may happen that the rotor shaft 12 also engages in the inoperative position during operation Fig. 3 shown position moves. Then, the projection 36 as an emergency bearing axial bearing in the opposite direction, in which it comes to rest on the impeller 4 facing axial side of the bearing ring 24, which is the axial side 28, which forms the actual thrust bearing surface, facing away.
  • Such an operating state can occur, in particular, when the pump unit starts up.
  • penetration of dirt into the bearing gap and the rotor space can be prevented.
  • annular seal 38 is shown, which is arranged circumferentially in this embodiment on the rotor shaft 12.
  • the seal 38 is arranged substantially in the region of the rotor 14 facing the axial end of the impeller 4 on the outer circumference of the rotor shaft 12.
  • this seal 38 comes in the region of the bearing gap on the bearing ring 24 sealingly to the plant.
  • Such a seal 38 could also be formed in the peripheral region of the rotor shaft 12 on the impeller 4, in particular be cast directly to the impeller 4 made of an elastic plastic.
  • Such a seal 38 could also be used as an alternative to the projection 36, as well as the projection 36 could be used without the seal 38.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Claims (17)

  1. Groupe motopompe comportant
    un moteur électrique d'entraînement qui comporte un stator (20) et un rotor réalisé sous la forme d'un rotor à aimant permanent (14),
    au moins une roue (4) qui est reliée au rotor (14) par un axe de rotor (12), et
    un palier axial (26, 28) qui est formé de façon à ce qu'il absorbe les efforts axiaux agissant, pendant le fonctionnement du groupe motopompe, sur la roue (4) et l'axe de rotor (12), et
    au moins un palier radial (22, 24) disposé au niveau de l'axe de rotor (12),
    le rotor (14) et le stator (20) étant formés de façon telle que, entre le rotor (14) et le stator (20) est généré un effort axial magnétique agissant dans le sens de l'axe de rotation (X) du rotor (14), qui agit sur le rotor dans la direction d'afflux (E) dans la roue (4),
    caractérisé en ce que l'axe de rotor (12) est supporté de façon à ce que le rotor (14) soit déplaçable dans la direction axiale (X) par rapport au stator (20), et l'axe du rotor (12) étant mobile de façon telle qu'il peut être déplacé de façon axiale, à l'état de repos du groupe motopompe, dans la direction d'afflux (E) dans la roue (4), et en ce que le palier radial (22, 24), au moins au nombre de un, est formé de façon telle que, en cas de déplacement axial de l'axe de rotor (12) dans la direction d'afflux (E) dans la roue, les surfaces de palier opposées (34) du palier radial (22, 24) se désaccouplent au moins partiellement.
  2. Groupe motopompe selon la revendication 1, caractérisé en ce qu'un effort axial hydraulique agissant, pendant le fonctionnement du groupe motopompe, sur la roue (4) et l'axe de rotor (12), est supérieur à l'effort axial magnétique orienté en sens opposé.
  3. Groupe motopompe selon la revendication 1 ou 2, caractérisé en ce que le stator (20) entoure le rotor (14) dans le sens périphérique.
  4. Groupe motopompe selon l'une des revendications précédentes, caractérisé en ce que, au niveau du rotor (14) et/ou du stator (20) est disposé au moins un élément magnétique dur ou doux supplémentaire qui contribue à générer l'effort axial magnétique.
  5. Groupe motopompe selon l'une des revendications précédentes, caractérisé en ce que le rotor (14) et le stator (20) sont formés et disposés de façon telle que, au moins pendant le fonctionnement du groupe motopompe, le milieu axial (MR) du rotor (14) est espacé du milieu axial (MS) du stator (20) dans la direction opposée à la direction d'afflux (E) dans la roue.
  6. Groupe motopompe selon l'une des revendications précédentes, caractérisé en ce que la roue, au moins au nombre de une, est fixée au niveau de l'axe de rotor (12) dans la direction axiale.
  7. Groupe motopompe selon l'une des revendications précédentes, caractérisé en ce que le palier axial (26, 28) est formé de façon telle que, en cas de déplacement de l'axe de rotor (12) dans la direction d'afflux (E) dans la roue, ses surfaces de palier (26, 28) se désaccouplent.
  8. Groupe motopompe selon l'une des revendications précédentes, caractérisé en ce que le palier radial (22, 24) est réalisé sous la forme d'un palier lisse dont une première surface de palier (34) est formée sur le pourtour extérieur de l'axe de rotor (12) et dont une seconde surface de palier, opposée, est formée dans une bague fixe de palier (22, 24).
  9. Groupe motopompe selon l'une des revendications précédentes, caractérisé en ce que, au moins au niveau d'un côté orienté vers la roue (4) d'une surface de palier (34), formée sur l'axe de rotor (12), du palier radial, le diamètre de l'axe de rotor (12) est réduit par rapport au diamètre de cette surface de palier (34).
  10. Groupe motopompe selon l'une des revendications précédentes, caractérisé en ce que les surfaces de palier opposées ont des dimensions d'étendue axiale telles et sont disposées l'une par rapport à l'autre de façon telle que, lors d'un déplacement axial de l'axe de rotor (12), elles se désaccouplent à plus de 50 %, de préférence à plus de 75 %.
  11. Groupe motopompe selon l'une des revendications précédentes, caractérisé en ce que, adjacent à la roue (4), est disposé un joint d'aspiration de façon telle que, en cas de déplacement axial de l'axe de rotor (12) dans la direction d'afflux (E) dans la roue (4), le joint d'aspiration (35) et la roue (4) se désaccouplent au moins partiellement.
  12. Groupe motopompe selon l'une des revendications précédentes, caractérisé en ce que l'axe de rotor (12) est déplaçable d'un montant qui est inférieur ou égal à une distance axiale (a) existant pendant le fonctionnement du groupe motopompe entre le milieu axial (MR) du rotor et le milieu axial (MS) du stator (20).
  13. Groupe motopompe selon l'une des revendications précédentes, caractérisé en ce que, au niveau de la roue (4), au moins au nombre de une, sur un côté axial orienté vers le rotor (12) est formée une surface d'appoint de palier (36) qui est orientée vers une surface de palier axial fixe.
  14. Groupe motopompe selon la revendication 13, caractérisé en ce que la surface de palier axial est formée par une face frontale axiale d'une bague de palier fixe (24) d'un palier radial et/ou axial de l'axe de rotor (12).
  15. Groupe motopompe selon la revendication 13 ou 14 et une des revendications 7 à 15, caractérisé en ce que la roue (4) est disposée par rapport à la bague de palier (24) de façon telle que la face d'appoint de palier (36) peut venir en contact avec la surface de palier axial fixe par le déplacement axial de l'axe de rotor (12), la surface d'appoint de palier (36), pendant le fonctionnement du groupe motopompe, étant de préférence espacée axialement de la surface de palier axial fixe.
  16. Groupe motopompe selon la revendication 15, caractérisé en ce que l'espacement de la surface d'appoint de palier (36) à la surface de palier axial fixe est inférieur ou égal à une distance axiale (a) existant pendant le fonctionnement du groupe motopompe entre le milieu axial (MR) du rotor et le milieu axial (MS) du stator (20).
  17. Groupe motopompe selon l'une des revendications précédentes, caractérisé en ce que, entre l'axe de rotor (12) ou la roue (4), d'une part, et une bague de palier fixe (24), d'autre part, est disposé au moins un élément d'étanchéité (38) qui est apte à être mis en appui rendant étanche par le déplacement axial de l'axe de rotor (12).
EP12813319.6A 2011-12-27 2012-12-19 Groupe de pompe Active EP2798224B2 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP12813319.6A EP2798224B2 (fr) 2011-12-27 2012-12-19 Groupe de pompe

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
EP11195804 2011-12-27
PCT/EP2012/076060 WO2013098142A1 (fr) 2011-12-27 2012-12-19 Groupe de pompe
EP12813319.6A EP2798224B2 (fr) 2011-12-27 2012-12-19 Groupe de pompe

Publications (3)

Publication Number Publication Date
EP2798224A1 EP2798224A1 (fr) 2014-11-05
EP2798224B1 EP2798224B1 (fr) 2016-03-23
EP2798224B2 true EP2798224B2 (fr) 2019-10-09

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Application Number Title Priority Date Filing Date
EP12813319.6A Active EP2798224B2 (fr) 2011-12-27 2012-12-19 Groupe de pompe

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US (1) US10024324B2 (fr)
EP (1) EP2798224B2 (fr)
CN (1) CN104024647B (fr)
WO (1) WO2013098142A1 (fr)

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EP3574217A4 (fr) * 2017-01-27 2020-11-25 Regal Beloit America, Inc. Ensembles pompes centrifuges dotés de moteur électrique à flux axial et leurs procédés d'assemblage
US10830252B2 (en) 2017-01-27 2020-11-10 Regal Beloit Australia Pty Ltd Centrifugal pump assemblies having an axial flux electric motor and methods of assembly thereof
US10584739B2 (en) 2017-01-27 2020-03-10 Regal Beloit Australia Pty Ltd Centrifugal pump assemblies having an axial flux electric motor and methods of assembly thereof
US10731653B2 (en) 2017-01-27 2020-08-04 Regal Beloit Australia Pty Ltd Centrifugal pump assemblies having an axial flux electric motor and methods of assembly thereof
US10865794B2 (en) 2017-01-27 2020-12-15 Regal Beloit Australia Pty Ltd Centrifugal pump assemblies having an axial flux electric motor and methods of assembly thereof
EP3376050A1 (fr) * 2017-03-14 2018-09-19 Grundfos Holding A/S Groupe pompe centrifuge
EP3376051B1 (fr) * 2017-03-14 2022-08-24 Grundfos Holding A/S Groupe motopompe
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EP3667090B1 (fr) * 2018-12-13 2021-07-07 Grundfos Holding A/S Ensemble de pompe
BE1030312B1 (de) * 2022-02-23 2023-10-02 Miele & Cie Strömungsmaschine

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Also Published As

Publication number Publication date
EP2798224B1 (fr) 2016-03-23
CN104024647A (zh) 2014-09-03
US20150017031A1 (en) 2015-01-15
WO2013098142A1 (fr) 2013-07-04
US10024324B2 (en) 2018-07-17
EP2798224A1 (fr) 2014-11-05
CN104024647B (zh) 2016-08-24

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