EP1767787B1 - Unité de pompe submersible - Google Patents

Unité de pompe submersible Download PDF

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Publication number
EP1767787B1
EP1767787B1 EP05020868A EP05020868A EP1767787B1 EP 1767787 B1 EP1767787 B1 EP 1767787B1 EP 05020868 A EP05020868 A EP 05020868A EP 05020868 A EP05020868 A EP 05020868A EP 1767787 B1 EP1767787 B1 EP 1767787B1
Authority
EP
European Patent Office
Prior art keywords
impeller
pump assembly
assembly according
axial
metallic material
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.)
Not-in-force
Application number
EP05020868A
Other languages
German (de)
English (en)
Other versions
EP1767787B2 (fr
EP1767787A1 (fr
Inventor
Helge Grann
Christian Rasmussen
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.)
Grundfos Management AS
Original Assignee
Grundfos Management AS
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
Family has litigation
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Application filed by Grundfos Management AS filed Critical Grundfos Management AS
Priority to AT05020868T priority Critical patent/ATE377152T1/de
Priority to EP05020868.5A priority patent/EP1767787B2/fr
Priority to DE502005001847T priority patent/DE502005001847D1/de
Priority to US12/067,868 priority patent/US8333575B2/en
Priority to CN2006800350691A priority patent/CN101273201B/zh
Priority to PCT/EP2006/009113 priority patent/WO2007033817A1/fr
Publication of EP1767787A1 publication Critical patent/EP1767787A1/fr
Publication of EP1767787B1 publication Critical patent/EP1767787B1/fr
Application granted granted Critical
Publication of EP1767787B2 publication Critical patent/EP1767787B2/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • 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
    • 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
    • F04D13/08—Units comprising pumps and their driving means the pump being electrically driven for submerged use
    • F04D13/086—Units comprising pumps and their driving means the pump being electrically driven for submerged use the pump and drive motor are both submerged
    • 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

Definitions

  • the invention relates to a pump unit with a wet-running electric motor.
  • Pump units with wet-running electric motors for example, as submersible pump units (such as in WO 99/25055 A1 ) or Schuungsumklalzpumpenaggregate trained.
  • submersible pump units such as in WO 99/25055 A1
  • a high delivery capacity with a compact design and low energy consumption is desirable.
  • several stages are usually provided in submersible pump units (such as in DE 8816412 U1 ). This leads to a more complicated structure of the pump unit, whereby the assembly is complex. On the other hand, the entire friction of the pump unit increases, whereby the power loss increases.
  • a high speed pump unit is off WO 02/052156 A1 known.
  • the pump unit according to the invention which has a wet-running electric motor, is provided with an impeller which can be driven by the wet-running electric motor with a maximum speed greater than 20,000 rpm, more preferably greater than 25,000 rpm or 30,000 rpm. Due to this high speed, a high flow rate of the pump can also be achieved with only one impeller small diameter can be achieved. By a small diameter of the impeller friction and thus losses of the pump unit can be minimized.
  • the impeller is axially sealed in the region of the suction mouth.
  • the axial sealing of the suction mouth has the advantage that the axial surface of the impeller, preferably the surface facing away from the electric motor, at the same time serve as a sealing surface, so that the number of required sealing elements is reduced and a simple and reliable seal in the suction mouth are formed can. This leads to a further reduction of friction and losses in the pump unit and thus to a higher overall efficiency.
  • At least one axial end face of the impeller particularly preferably forms an axial bearing surface.
  • the bearing surface simultaneously serves as an axial sealing surface. This has the further advantage that no additional pressure elements are required to hold the seal in abutment.
  • the thrust bearing which forms a sliding bearing, automatically sets a sufficiently small gap, which ensures a reliable seal and at the same time ensures a sufficient lubricating film on the bearing surface.
  • the gap is preferably in the range of a few micrometers. This ensures a particularly good seal at the suction mouth, which further contributes to increase the efficiency of the pump unit.
  • the impeller is formed on its axial side on which the impeller blades are arranged open and form the axial end faces of the impeller blades a thrust bearing surface of the impeller.
  • the axial free end faces of the impeller blades serve for the axial bearing of the impeller and thus the rotor shaft and at the same time the sealing of the impeller on its open end.
  • a very good seal is achieved very easily, since the impeller blades are pressed by the axial force which is to be absorbed by the thrust bearing against an opposite thrust bearing surface, for example a counter-rotating disc.
  • a very small gap is created between the axial end faces of the blades and the counter-rotating disc, which preferably simultaneously ensures good sealing and a sufficient lubricating film in the axial sliding bearing.
  • the impeller is fixed on the rotor shaft in the axial direction, so that the impeller can take over the axial bearing function of the entire rotor. That is, the axial bearing of the entire rotor takes place on the impeller, preferably in a sliding bearing, whose thrust bearing surface is formed by the axial end face of the impeller, preferably from the axial end faces of the impeller blades.
  • the electric motor facing the axial end face of the impeller is designed as a sealing surface for sealing the rotor space of the electric motor. That is, an axial sealing surface is preferably also provided here, against which a stationary sealing element, for example a sealing ring, rests. This sealing ring can be pressed by spring preload or elastic residual stress against the sealing surface.
  • the sealing of the rotor space is preferred in order to prevent impurities from the fluid to be delivered by the pump unit, which is preferably water, from penetrating into the rotor space where it may lead to undesired friction or possibly even damage to the rotor.
  • the rotor chamber can be factory-fitted with fluid be prefilled.
  • the fluid it is possible for the fluid to enter the rotor space when the pump unit is first started up.
  • This can be ensured by the fact that the seal between impeller and rotor space is not formed completely fluid-tight, but only designed so that no contamination or only small amounts of fluid can enter the rotor space.
  • the fluid exchange between the pump chamber, in which the impeller rotates, and the rotor space in the interior of the split tube is minimized or prevented.
  • the fact that the sealing surface is provided directly on the impeller, a very simple seal with a minimized number of components can be ensured.
  • it can be ensured by the sufficient sealing, that it does not come to friction losses due to contamination, whereby a high efficiency of the pump unit can be permanently ensured.
  • the impeller particularly preferably has at least one surface made of hard metal or ceramic and is preferably made entirely of hard metal or ceramic. This configuration allows the wear of the impeller blades due to contamination in the fluid, such as sand particles to minimize or prevent.
  • the particularly hard or wear-resistant design of the impeller surfaces allows use as Gleitlager- or thrust bearing surfaces, so that can be dispensed with additional bearing shells or bearing elements.
  • the wear-resistant design of the impeller also allows to further increase the speed of the impeller without causing greater wear. This makes it possible to increase the efficiency of the pump unit, without the need to provide further stages. At the same time, the impeller can be made very small. A small impeller diameter leads to the reduction of friction losses, whereby the efficiency of the pump unit can be further increased.
  • a hardness of the impeller surface is preferably greater than 1000 HV.
  • the design of the impeller completely made of hard metal or ceramic can be carried out, for example, in the sintering process, wherein the impeller blades are then preferably ground to form the end faces of the impeller blades as defined Axiallager- and sealing surface. If the opposite end face of the impeller is also to be formed as a sealing surface, these are also preferably ground to create a defined contact surface.
  • the pump unit according to the invention particularly preferably has only one step.
  • the number of required items is significantly reduced.
  • the friction occurring throughout the pump unit is reduced, whereby the efficiency can be increased.
  • the impeller preferably also has a very small diameter, whereby the power loss further reduced and at the same time the operation is promoted at high speed.
  • the diameter of the rotor is formed very small.
  • the friction losses in the engine are minimized and the high-speed operation favors.
  • the rotor diameter is less than 25 mm, more preferably less than 20 mm. The smaller the rotor diameter, the lower the friction that occurs.
  • the reduced diameter electric motor can be made longer in the axial direction.
  • a very stiff rotor shaft is preferably provided.
  • Such a very rigid rotor shaft can be achieved by integrally forming the rotor shaft, including the axial end on which the impeller is mounted, ideally in one piece with the entire rotor.
  • the pump unit preferably has an electric motor with a permanent magnet rotor. This allows a simple construction of the engine.
  • the diameter of the permanent magnet rotor is preferably chosen as small as possible in order to minimize the friction. Particularly preferred is a diameter smaller than 25 mm.
  • particularly strong permanent magnets such as neodymium magnets can be used.
  • the pump unit according to the invention is preferably designed as a submersible pump unit. Especially with submersible pump units, a high delivery rate is often desired.
  • a counter-rotating disc facing the impeller is provided, which abuts on an axial side of the impeller, preferably the axial side facing away from the electric motor, in such a way that it forms an axial bearing surface.
  • a sliding bearing is formed between the axial end face of the impeller or the impeller blades and the mating disk, which can serve as a thrust bearing of the impeller and the entire rotor.
  • the counter-rotating disc preferably also has at least one surface made of hard metal or ceramic material in order to be able to ensure the wear characteristics required for a sliding bearing or sealing surface, even at high rotational speeds. It is also possible to form the counter-rotating disc completely made of hard metal or ceramic material. Particularly preferred only the impeller facing part of the counter-rotating disk is formed from such a material. The part facing away from the impeller may be formed of a different material or metal and be glued to the impeller facing part, for example. Alternative methods or designs which ensure a sufficient hardness or wear resistance of the surface of the counter-rotating disc can also be used here.
  • the impeller facing away from the axial side of the mating disk is preferably spherical, ie in particular formed hemispherical. This allows the mating disk to be stored in a corresponding spherical or hemispherical receptacle, so that a self-centering or self-alignment of the mating disk is achieved parallel to the impeller or the axial end face of the impeller. On the one hand this simplifies assembly and on the other hand ensures wear-free and safe operation of the pump unit even at high speeds.
  • the impeller is surrounded by a spiral housing or diffuser, whereby the radially discharged from the impeller funded fluid is deflected so that it can be preferably forwarded in the axial direction and out of the pump unit in a connecting line.
  • the impeller is particularly preferably surrounded by a spiral housing, which extends helically in such a way that the outlet opening of the spiral housing in the axial direction to the impeller, d. H. aligned parallel to its axis of rotation.
  • This has the effect that the fluid which exits the impeller in the tangential / radial direction is deflected by the volute as loss-free as possible to form an axially directed outlet opening of the pump unit.
  • the pump unit to a wet-running electric motor with a split tube, which is made of a non-metallic material, wherein the non-metallic material is provided with at least one additional hermetically sealing layer.
  • the canned tube according to the invention thus preferably consists of a non-metallic material, ie of a material which influences the magnetic field between rotor and stator as little as possible or not. The fact that the magnetic field is unaffected by the canned material, efficiency deterioration due to the arrangement of the can between stator and rotor are avoided.
  • the hermetically sealing layer which is preferably applied to the outer or the inner peripheral surface or on both peripheral surfaces, makes it possible to use a material for the split tube, which does not have the sufficient diffusion tightness per se. That is, it can be a material to be selected, which ensures primarily a sufficient stability of the can.
  • the diffusion-tightness in such a way that inside the can, d. H. Fluid in the rotor space can not penetrate through the gap tube in the stator, is achieved by the additional, preferably applied to the surface of the non-metallic material layer.
  • multiple layers of different materials may be used in combination to achieve the desired hermetic seal between the interior of the can and the outer peripheral portion of the can.
  • the Spaltrohrwandung can be constructed of multi-layer of non-metallic material and one or more layers of other materials that ensure the diffusion-tightness.
  • the diffusion-tight layer which ensures the hermetic seal, be formed of a special plastic or paint.
  • the diffusion-proof layer may also be formed, for example, as a tube, foil or foil pot, in particular of metal.
  • the non-metallic material can be applied after the production or shaping of the non-metallic material on this. Furthermore, it is possible to incorporate a foil or a tube into the non-metallic material even during the shaping thereof so that the hermetically sealing layer covers the tube or the foil on one or both sides or peripheral sides.
  • the tube or foil may be disposed inside the non-metallic material. This can be done, for example, during the injection molding of the non-metallic material.
  • the at least one layer is formed as a coating on the inner and / or outer peripheral surface of the non-metallic material.
  • a coating can be applied after the production or molding of the part of non-metallic material on the surface, for example by spraying or vapor deposition.
  • the coating is formed as a metallization of the non-metallic material. That is, on the inner and / or outer peripheral surface of the can, a metal layer is applied, for example vapor-deposited. This metal layer then ensures the hermetic seal.
  • the coating of the non-metallic material for example by metallization with a suitable metal, is advantageously carried out so that the entire peripheral surface, which forms the separation between the rotor space in the interior of the can and the surrounding stator space, is coated accordingly, so that no fluid in this area For example, water from the interior of the can through the Spaltrohrwandung can penetrate into the surrounding stator space. In this way it is possible to use stators without potting compound.
  • the can is made of plastic and preferably a fiber-reinforced plastic.
  • Plastic allows cost-effective production of the can, for example by injection molding. Furthermore, plastic has no magnetic properties and therefore does not affect the magnetic field between the stator and the rotor. Furthermore, plastic can be suitably coated or provided with further surrounding and internal plastic layers, in the manner of coextrusion. Even a metallization of plastic is easily possible.
  • the fiber-reinforced construction can improve the stability or pressure resistance of the can.
  • the split tube is made of a tubular member and a bottom member which closes the tubular member at a first axial end.
  • This allows a simplified production of the can, which allows, for example, the production of thin-walled plastic split tubes by injection molding.
  • injection molding of the can it may be appropriate that a core forming the cavity in the interior of the can, at both axial Ends of the can is held in order to achieve a very thin-walled design of the can.
  • the tubular component is manufactured and then later the bottom element is inserted into this tubular component in order to close an axial opening of the tubular component and to form a canned pot.
  • the opposite axial side of the can is open, so that the rotor shaft can extend to the pump space through this axial side.
  • the bottom element may be force, positively and / or materially inserted into the tubular member, so that a solid stable and preferably tight connection between the tubular member and the bottom element is provided.
  • the bottom element is potted with the tubular component.
  • the bottom element in a second manufacturing step by injection molding on the tubular member molded or molded or poured into the tubular member, so that a permanent tight connection between the two elements is created.
  • the tubular component and the bottom element are more preferably both made of a non-metallic material, preferably plastic and provided after assembly together with the additional layer or coating.
  • the region of the base element and in particular the transition region between the tubular component and the base element are also hermetically sealed by the coating.
  • the tubular component and the bottom element can be metallized together.
  • the additional layer can be attached to the floor element separately or integrated into this.
  • a further preferred embodiment is at an axial end of the can, preferably at the pump room and The impeller of the pump facing the end, on the outer circumference, a radially outwardly extending, preferably formed metallic collar.
  • This metallic collar is used for.
  • B. the frontal closure of the stator housing, in which the stator winding is arranged.
  • the stator housing is preferably hermetically encapsulated, in particular when used in a submersible pump, so that no fluid can penetrate into the interior of the stator housing. Thus, the coils are protected inside the stator housing in particular from moisture.
  • the metallic collar which is mounted on the outer circumference of the can, serves to connect to the outer parts of the stator housing and allows the can to be welded to the rest of the stator housing.
  • the collar is preferably positively and / or materially connected to the non-metallic material and provided together with this with the additional layer or coating.
  • a non-positive connection is conceivable, provided sufficient strength and tightness is ensured.
  • the common coating of the non-metallic material of the can and of the collar has the advantage that in particular the transition region between the non-metallic material and the collar is hermetically sealed by the coating. In order to ensure a permanent seal in this area, a particularly strong connection between the metallic collar and the non-metallic material of the split tube is preferred, so that movements between the two elements, which could lead to cracking of the coating, are avoided.
  • the metallic collar is preferably connected directly to the non-metallic material during manufacture of the can.
  • the metallic collar can be inserted into the mold prior to injection molding and the plastic molded onto the collar or a part of the collar are molded with plastic, so that directly achieved in injection molding a positive and fluid connection between the two elements becomes.
  • a surface of the collar is preferably patterned or roughened prior to bonding to the non-metallic material of the can. This can be done for example by laser irradiation, wherein by means of a laser beam small depressions and / or crater-shaped elevations are introduced into the surface of the collar into which flows the non-metallic material, such as plastic during casting and thus on the one hand over a larger surface and on the other a positive connection establishes a firm connection with the collar.
  • Fig. 1 shows a sectional view of the upper end of a submersible pump.
  • the lower end in which the electronics for controlling the pump is mounted, is not shown in the figure.
  • the pump unit has at its upper end a connecting piece 2 with a non-return valve 4 arranged therein.
  • a spiral housing 6, which surrounds the impeller 8, adjoins the inside of the pump assembly upstream.
  • the impeller 8 is arranged at the axial end of the integral rotor shaft 10 of the electric motor 11 or its permanent magnet rotor 12.
  • the impeller 8 is fixedly fixed to the rotor shaft 10, in particular in the axial direction X firmly connected.
  • the permanent magnet rotor 12 runs in the interior of a split tube 14 which is surrounded annularly by the stator 16 on its outer circumference.
  • the stator 16 is formed in a known manner as a laminated core with coil windings.
  • the stator 16 is hermetically sealed in total in a stator housing 18.
  • the rotor shaft 10 is mounted in two radial bearings 20 in the radial direction. These radial bearings 20 are preferably self-centering, so that easy assembly and safe operation is ensured even at high speeds.
  • the split tube 14 is, as shown in detail in Figures 2 and 3, formed in the example shown from plastic.
  • the split tube is formed from a tubular component 22, which is made of fiber-reinforced plastic by injection molding.
  • the tubular component 22 is initially formed with open axial ends 24 and 26. This allows a core, which forms the interior 28 of the can 14, which later forms the rotor space, to be fixed at both axial ends in the tool.
  • After this Injection molding of the tubular member 22 is then closed at the axial end 24 by a bottom member 30, so that a canned pot is formed.
  • the bottom element 30 may preferably also be made of plastic and cast into the previously molded tubular component 2.
  • the bottom member 30 may be manufactured separately and later inserted into the tubular member 22. As shown, a positive connection between bottom element 30 and tubular component 22 is produced in that the inwardly bent axial peripheral edge of the tubular component 22 engages in a circumferential groove 32 of the bottom element 30.
  • a collar 34 is attached to the outer circumference of the tubular member 22.
  • the collar 34 is formed of metal, preferably stainless steel and annular, with its inner diameter is matched to the outer diameter of the tubular member 22 at the axial end 26.
  • the ring of the collar 34 has a U-shaped cross-section, wherein the transverse leg faces the axial end 26.
  • the inner wall 36 of the collar 34 abuts parallel to the peripheral wall of the tubular member 22 and is connected thereto.
  • connection between the inner wall 36 of the collar 34 and the tubular member 22 takes place already during the manufacturing, ie casting process of the tubular member 22 by previously the collar 34 is inserted into the tool, so that the tubular member 22 directly to the inner wall 36th the collar 34 is poured.
  • a solid positive and / or cohesive connection between the plastic of the tubular member 22 and the inner wall 36 of the collar 34 is provided.
  • the inner wall 36 is roughened on its inner circumference before or structured. This can preferably be done by laser processing, by means of which in the metal or the sheet of the collar 34 on the surface small recesses are introduced, in which then the plastic of the tubular member 22 flows during injection molding.
  • These recesses may particularly preferably also have undercuts, by which an even firmer connection between the two elements is created.
  • the gap tube 14 thus created is metallized.
  • a thin metal layer 38 is applied to the outer surface of the can 14, as shown in Fig. 3.
  • the metal layer 38 covers the entire outer surface of the tubular component 22 and the bottom element 30 and the collar 34.
  • the metal layer 38 ensures that a hermetic seal of the can 14 and in particular the peripheral wall of the tubular member 22 is provided.
  • This hermetic seal through the metal layer 38 causes fluid, which is located in the rotor chamber 28, can not penetrate through the split tube 14 into the interior of the stator housing 18, in which the stator 16 is arranged.
  • the metallization or coating 38 allows the use of a plastic for the tubular member 22 and the bottom member 30, which is not diffusion-tight per se. So here the plastic can be selected purely according to the requirements of the stability of the can 14 and according to manufacturing considerations.
  • split tube 14 has been described, which is provided on its outside with the metal layer 38.
  • metal layer 38 it is also possible to provide the split tube 14 both on its outer side and on the inner surfaces of the inner space 28 with a metal layer by metallization.
  • the metallic collar 34 serves to connect the split tube 14 with the remaining part of the stator housing 18. This can be done in particular by a weld 39 on the outer circumference of the metallic collar 34.
  • the collar 34 thus provides the connection to other metallic components from which the stator housing 18 is formed, as shown in Fig. 4.
  • the use of the can 14 of plastic, d. H. a non-metallic material without magnetic properties has the advantage that the gap tube 14, the magnetic field between stator 16 and permanent magnet rotor 12 only slightly or not affected, whereby the efficiency of the electric motor 11 is increased.
  • the diameter of the permanent magnet rotor 12 and the impeller 8 is kept small in order to minimize the friction in the system and thus the power loss as possible.
  • the permanent magnet rotor 12 is equipped with particularly strong permanent magnets, for example neodynium magnets. In the example shown, the rotor diameter is 19 mm.
  • the electric motor 11 shown is designed for very high speeds> 20,000, in particular between 25,000 and 30,000 rpm. Thus, with only one impeller 8 with a relatively small diameter, a sufficiently high flow rate can be achieved.
  • the impeller 8 which is shown in Figures 5 and 6 as a single part, is made of hard metal to ensure high wear resistance.
  • the impeller 8 is open, d. H. the impeller blades project from the axial side 40 of the impeller 8 and are not closed at their end faces 44 by a cover.
  • the end faces or end edges 44 of the impeller blades 42 are ground and thus form a Axiallager- and sealing surface of the impeller 8.
  • the end faces 44 are in the installed state of a counter-rotating disk 46, which surrounds the suction port 48 of the pump annular. Due to the fixed connection of the impeller 8 with the rotor shaft 10, the entire rotor 12 is supported via the impeller 8 in the axial direction on the counter-rotating disk 46. Ie. the end face of the mating disk 46, which faces the impeller 8, and the end faces 44 of the impeller blades 42 form an axial sliding bearing.
  • the end faces 44 of the impeller blades 42 are pressed against the mating disk 46 so that there is a particularly good seal between the impeller blades 42 and the counter-rotating disk 46.
  • losses in the pump are minimized and the delivery rate of the pump unit is further increased, especially at the high engine speed described above.
  • the impeller 8 assumes the a-xial workede seal against the mating disk 46 at the suction port 48 and at the same time the thrust bearing function, so that here the number of components and the friction occurring are minimized.
  • the impeller blades 42 facing away from the back 50 of the impeller 8 has a further annular sealing surface 52, which the opening 54 annularly surrounds for receiving the rotor shaft.
  • the sealing surface 52 bears against a seal 56, which surrounds the rotor shaft 10 fixedly and seals off the rotor chamber 28 in the interior of the can 14 for the pump chamber, in which the impeller 8 is arranged.
  • This seal 56 is held by spring action on the sealing surface 52 in abutment.
  • the seal 56 ensures that impurities in the fluid, which is conveyed by the impeller 8, penetrate into the rotor chamber 28 in the interior of the can 14 and there may lead to undesirable friction or damage.
  • the counter-rotating disc 46 is also preferably made of hard metal or ceramic.
  • the side facing away from the impeller 8 58 is spherically formed (not shown in Fig. 1) and mounted in a spherical receptacle in the pump housing, so that the mating disk 46 can align automatically parallel to the impeller 8.
  • This part of the counter-rotating disc, which forms the back 58 may be formed of a material other than cemented carbide or ceramic and connected to the part of the counter-rotating disc 46, which faces the impeller 8, for example by gluing.
  • the impeller 8 is circumferentially surrounded by the spiral housing 6.
  • the spiral housing 6 extends, starting from the peripheral region of the impeller 8, helically to the connecting piece 2, so that a flow deflection takes place in the axial direction. Ie. the flow, which exits in the radial / tangential direction on the outer circumference of the impeller 8, is first deflected by the volute 6 in a purely tangential direction or circumferential direction of the impeller 8 and then steered in the axial direction as lossless as possible due to the helical winding of the volute 6, so that the flow at the connecting piece 2 in the axial direction can escape from the pump unit.
  • the spiral housing 6 is preferably also made of plastic as an injection molded part.
  • the spiral housing 6 further includes at its lower, the impeller 8 facing end also spherical receptacle for the mating disk 6 and centrally forms the suction port 48 of the pump, through which the fluid is sucked by rotation of the impeller 8.
  • the outer housing of the pump unit has in the region in which the spiral housing 6 is disposed in its outer peripheral wall inlet opening 62, through which the fluid enters from the outside, flows around the spiral housing 6 from the outside and then enters the suction mouth 48 ,

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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)
  • Eye Examination Apparatus (AREA)

Claims (24)

  1. Groupe moto-pompe comprenant un moteur électrique à fonctionnement en milieu humide, caractérisé en ce qu'une roue à aubes (8) du groupe moto-pompe peut être entraînée, par le moteur électrique (11), à une vitesse de rotation maximale supérieure à 20 000 t/min et la roue à aubes (8) est étanchéifiée axialement dans la région de la bouche d'aspiration (48).
  2. Groupe moto-pompe selon la revendication 1, caractérisé en ce qu'au moins une face frontale axiale (44) de la roue à aubes (8), forme une surface de butée axiale qui, de préférence, sert en même temps de surface d'étanchéité axiale.
  3. Groupe moto-pompe selon la revendication 2, caractérisé en ce que la roue à aubes (8) est prévue ouverte sur sa face axiale (40), sur laquelle des aubes (42) de roue à aubes sont disposées, et les faces frontales axiales (44) des aubes de roues à aubes forment une surface de butée axiale de la roue à aubes (8).
  4. Groupe moto-pompe selon l'une des revendications précédentes, caractérisé en ce que la roue à aubes (8) est immobilisée en direction axiale (X) sur un arbre de rotor (10).
  5. Groupe moto-pompe selon l'une des revendications précédentes, caractérisé en ce que la face frontale axiale (50), tournée vers le moteur électrique (11), de la roue à aubes (8) est aménagée sous forme d'une surface d'étanchéité (52), pour l'étanchéification du logement (28) du rotor du moteur électrique (11).
  6. Groupe moto-pompe selon l'une des revendications précédentes, caractérisé en ce que la roue à aubes (8) présente au moins une surface en métal dur ou en céramique et, de préférence, est entièrement réalisée en métal dur ou en céramique.
  7. Groupe moto-pompe selon l'une des revendications précédentes, caractérisé en ce qu'il présente un seul étage.
  8. Groupe moto-pompe selon l'une des revendications précédentes, caractérisé en ce qu'il présente un moteur électrique (11) comprenant un rotor à aimants permanents (12).
  9. Groupe moto-pompe selon l'une des revendications précédentes, caractérisé en ce qu'il est conçu en groupe moto-pompe submersible.
  10. Groupe moto-pompe selon l'une des revendications précédentes, caractérisé en ce qu'il est prévu un disque à rotation opposée (46) tourné vers la roue à aubes (8), lequel s'applique contre une face axiale (44) de la roue à aubes de manière à définir une surface de butée axiale.
  11. Groupe moto-pompe selon la revendication 10, caractérisé en ce que le disque à rotation opposée (46) présente au moins une surface en un métal dur ou un matériau céramique.
  12. Groupe moto-pompe selon la revendication 10 ou 11, caractérisé en ce que la face axiale (58) du disque à rotation opposée (46), tournée à l'opposé de la roue à aubes (8), est dotée d'une forme sphérique.
  13. Groupe moto-pompe selon l'une des revendications précédentes, caractérisé en ce que la roue à aubes (8) est entourée d'un carter en volute (6) ou d'un dispositif directeur.
  14. Groupe moto-pompe selon la revendication 13, caractérisé en ce que la roue à aubes (8) est entourée d'un carter en volute (6) qui s'étend sous une forme hélicoïdale d'une manière telle, que l'ouverture de sortie du carter en volute (6) soit orientée en direction axiale (X) par rapport à la roue à aubes (8).
  15. Groupe moto-pompe selon l'une des revendications précédentes, caractérisé en ce qu'il présente un moteur électrique à fonctionnement en milieu humide (11) comportant une gaine (14), qui est réalisée en un matériau non métallique, le matériau non métallique étant pourvu d'au moins une couche (38) additionnelle hermétiquement étanchéifiante.
  16. Groupe moto-pompe selon la revendication 15, caractérisé en ce que ladite au moins une couche additionnelle est constituée sous forme d'un revêtement (38) sur la surface périphérique intérieure et/ou extérieure du matériau non métallique (22).
  17. Groupe moto-pompe selon la revendication 16, caractérisé en ce que le revêtement (38) est produit sous forme d'une métallisation du matériau non métallique.
  18. Groupe moto-pompe selon l'une des revendications 15 à 17, caractérisé en ce que la gaine (14) est réalisée en matière plastique et, de préférence, en une matière plastique renforcée par des fibres.
  19. Groupe moto-pompe selon l'une des revendications 15 à 18, caractérisé en ce que la gaine est réalisée à partir d'une pièce tubulaire (22) et d'un élément de fond (30), qui ferme la pièce tubulaire (22) à une première extrémité axiale (24).
  20. Groupe moto-pompe selon la revendication 19, caractérisé en ce que l'élément de fond (30) est coulé avec la pièce tubulaire (22).
  21. Groupe moto-pompe selon la revendication 19 ou 20, caractérisé en ce que la pièce tubulaire (22) et l'élément de fond (30) sont réalisés en un matériau non métallique, de préférence en matière plastique, et sont, après l'assemblage, pourvus conjointement de la couche additionnelle ou du revêtement (38).
  22. Groupe moto-pompe selon l'une des revendications 15 à 21, caractérisé en ce qu'à une extrémité axiale (26) de la gaine (14) est formée, sur la surface périphérique extérieure, une collerette (34), de préférence métallique, s'étendant radialement vers l'extérieur.
  23. Groupe moto-pompe selon la revendication 22, caractérisé en ce que la collerette (34) est jointe par solidarisation mécanique et/ou par solidarisation de matière au matériau non métallique et est pourvue de la couche additionnelle ou du revêtement (38) en commun avec ce dernier.
  24. Groupe moto-pompe selon la revendication 22 ou 23, caractérisé en ce qu'une surface (36) de la collerette (34) est structurée avant la jonction au matériau non métallique de la gaine (14), de préférence par exposition à un faisceau laser.
EP05020868.5A 2005-09-24 2005-09-24 Unité de pompe submersible Not-in-force EP1767787B2 (fr)

Priority Applications (6)

Application Number Priority Date Filing Date Title
AT05020868T ATE377152T1 (de) 2005-09-24 2005-09-24 Pumpenaggregat
EP05020868.5A EP1767787B2 (fr) 2005-09-24 2005-09-24 Unité de pompe submersible
DE502005001847T DE502005001847D1 (de) 2005-09-24 2005-09-24 Pumpenaggregat
CN2006800350691A CN101273201B (zh) 2005-09-24 2006-09-20 泵装置
US12/067,868 US8333575B2 (en) 2005-09-24 2006-09-20 Pump assembly
PCT/EP2006/009113 WO2007033817A1 (fr) 2005-09-24 2006-09-20 Groupe motopompe

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP05020868.5A EP1767787B2 (fr) 2005-09-24 2005-09-24 Unité de pompe submersible

Publications (3)

Publication Number Publication Date
EP1767787A1 EP1767787A1 (fr) 2007-03-28
EP1767787B1 true EP1767787B1 (fr) 2007-10-31
EP1767787B2 EP1767787B2 (fr) 2016-10-26

Family

ID=35586235

Family Applications (1)

Application Number Title Priority Date Filing Date
EP05020868.5A Not-in-force EP1767787B2 (fr) 2005-09-24 2005-09-24 Unité de pompe submersible

Country Status (6)

Country Link
US (1) US8333575B2 (fr)
EP (1) EP1767787B2 (fr)
CN (1) CN101273201B (fr)
AT (1) ATE377152T1 (fr)
DE (1) DE502005001847D1 (fr)
WO (1) WO2007033817A1 (fr)

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EP2297466A1 (fr) * 2008-05-06 2011-03-23 FMC Technologies, Inc. Système de balayage
CN101825513A (zh) * 2010-05-21 2010-09-08 哈尔滨东安发动机（集团）有限公司 一种水泵总成的气密性检查方法
EP2472055B1 (fr) * 2010-12-30 2013-08-07 Welltec A/S Outil de levage artificiel
US9601951B2 (en) 2013-11-04 2017-03-21 General Electric Company Modular permanent magnet motor and pump assembly
DE102013020387A1 (de) * 2013-12-10 2015-06-11 Wilo Se Nassläufermotorpumpe
DE102016105309A1 (de) * 2016-03-22 2017-09-28 Klaus Union Gmbh & Co. Kg Magnetkupplungspumpe
CN112106279B (zh) 2018-02-23 2023-10-27 提取管理有限责任公司 电潜式泵送单元
CN109386497A (zh) * 2018-11-09 2019-02-26 合肥工业大学 一种含有复合式叶轮转子的脱硫泵
EP3763943A1 (fr) * 2019-07-10 2021-01-13 Grundfos Holding A/S Procédé de fabrication d'une chemise d'entrefer

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Also Published As

Publication number Publication date
CN101273201A (zh) 2008-09-24
CN101273201B (zh) 2013-04-24
WO2007033817A1 (fr) 2007-03-29
US20090035161A1 (en) 2009-02-05
EP1767787B2 (fr) 2016-10-26
DE502005001847D1 (de) 2007-12-13
US8333575B2 (en) 2012-12-18
ATE377152T1 (de) 2007-11-15
EP1767787A1 (fr) 2007-03-28

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