EP3475570A1 - Dispositif de pompage - Google Patents

Dispositif de pompage

Info

Publication number
EP3475570A1
EP3475570A1 EP17731899.5A EP17731899A EP3475570A1 EP 3475570 A1 EP3475570 A1 EP 3475570A1 EP 17731899 A EP17731899 A EP 17731899A EP 3475570 A1 EP3475570 A1 EP 3475570A1
Authority
EP
European Patent Office
Prior art keywords
pumping
drive
hollow shaft
pump
cartridges
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.)
Withdrawn
Application number
EP17731899.5A
Other languages
German (de)
English (en)
Inventor
Karsten Laing
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.)
Xylem Europe GmbH
Original Assignee
Xylem IP Management SARL
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
Priority claimed from DE102016111427.8A external-priority patent/DE102016111427A1/de
Priority claimed from DE102016111440.5A external-priority patent/DE102016111440A1/de
Priority claimed from DE102016111408.1A external-priority patent/DE102016111408A1/de
Priority claimed from DE102016111419.7A external-priority patent/DE102016111419A1/de
Priority claimed from DE102016111406.5A external-priority patent/DE102016111406A1/de
Priority claimed from DE102016111445.6A external-priority patent/DE102016111445A1/de
Priority claimed from DE102016111414.6A external-priority patent/DE102016111414A1/de
Application filed by Xylem IP Management SARL filed Critical Xylem IP Management SARL
Publication of EP3475570A1 publication Critical patent/EP3475570A1/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D13/00—Pumping installations or systems
    • F04D13/02—Units comprising pumps and their driving means
    • F04D13/06—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
    • 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
    • F04D13/0693—Details or arrangements of the wiring
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B17/00—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
    • F04B17/03—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B47/00—Pumps or pumping installations specially adapted for raising fluids from great depths, e.g. well pumps
    • F04B47/06—Pumps or pumping installations specially adapted for raising fluids from great depths, e.g. well pumps having motor-pump units situated at great depth
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/06—Control using electricity
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/16—Casings; Cylinders; Cylinder liners or heads; Fluid connections
    • 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
    • F04D13/10—Units comprising pumps and their driving means the pump being electrically driven for submerged use adapted for use in mining bore holes
    • 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
    • F04D25/0693—Details or arrangements of the wiring
    • 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
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2240/00—Components
    • F05D2240/60—Shafts
    • F05D2240/61—Hollow

Definitions

  • the invention relates to a pumping device for conveying a fluid, for example from a borehole. Due to the large variety of different locations and application parameters, such as flow rate and pressure to be overcome, and the often limited space available a large variety of pumping devices is necessary. Such pumping devices are used, for example, as borehole pumps. Depending on the requirements of the pump and the pumping capacities, a large number of pump stages are required, depending on the application. For this reason, the drive shaft usually has to be mounted on a plurality of pumps between the pumping stages in order to ensure safe operation of the pumping device. This in turn means that during the assembly of the pumping device an exact sequence of pumping elements and bearings must be maintained, which can only be ensured under controlled conditions with sufficient certainty.
  • the electrical supply device is guided from the connection section along an outer wall of the pumping device to the drive, whereby the space available for the actual pumping device space is limited.
  • the invention has for its object to provide a pumping device, is optimally utilized in the available space.
  • the drive shaft is or comprises a hollow shaft and that the electrical supply device runs within the drive shaft.
  • the electrical supply device does not have to be guided on the outside of a wall of the pump device. This results in a better one - -
  • a higher pumping power of the pump device can then be achieved if space is provided for the electrical supply device in the vicinity of the axle, as in this case within the hollow shaft, since the pump power and drive power achievable in this area are low.
  • a possibly provided motor control can be arranged behind the drive as seen from the connection section, so that the motor control can be positioned outside the flow path of the fluid to be pumped.
  • An advantageous solution provides that a motor control and an electrical connection of the pumping device are electrically connected to one another by the electrical supply device. Thereby, the transmission of electrical energy can be performed within the pumping device from the supply line to the consumer.
  • control signals sent to the pumping device may be forwarded to the engine controller.
  • a particularly advantageous possibility provides that the electrical connection of the pumping device is arranged in the connection section.
  • a fluid line and an electrical supply device can be laid from the same area of the pumping device, resulting in further space savings.
  • the electrical supply line device extends from the connection section, starting through the pumping element and through an electric motor of the drive. This is advantageous because Both the pumping element and the electric motor are more effective when the electrical supply device runs inside the drive shaft than when it would run outside.
  • the at least one pumping element comprises an impeller. Since an impeller is a pumping element that works on the principle of flow pumps, no valves or flaps are needed. Moreover, with an impeller, the effectiveness depends on the distance to the axis of rotation of the impeller, so that the effect of the central guidance of the electrical supply device comes to full advantage.
  • the connection section comprises a central fluid outlet opening, to which a hose or pipe connection can be fixed or fixed, into which the fluid to be pumped can be introduced. In this way, the fluid to be pumped can be introduced into a conduit through which the fluid to be pumped can be guided to the destination.
  • a particularly advantageous solution provides that within the hollow shaft and coaxial with the hollow shaft, a central armature is arranged and that the electrical supply device extends in a free space between the central armature and the hollow shaft. This is advantageous because it is unproblematic for the electrical properties when an electrical conductor is formed flat and by this arrangement of central armature and electrical supply means within the hollow shaft advantageous for the stability of the central armature design of the central anchor is possible.
  • an electrical conductor of the electrical supply device is arranged in the circumferential direction uniformly around the armature.
  • at least two electrical conductors are provided.
  • an electrical conductor of the electrical supply device has a circular arc segment-like cross section.
  • the circular arc segment-like cross-section of a - - electrical conductor is optimally adapted to the limited space within the hollow shaft.
  • a favorable possibility for the transmission of electrical energy provides that an electrical conductor of the electrical supply device are electrically insulated at least within the drive shaft.
  • an inner insulating layer is arranged between electrical conductors of the electrical supply device and the central armature, since in this way the electrical conductors can be arranged supported on the central armature via the insulating layer.
  • an outer insulating layer is arranged, which does not touch the hollow shaft.
  • the electrical conductors are thus electrically insulated around their entire circumference. The fact that the insulating layer does not touch the hollow shaft, this insulating layer is not damaged and there is no storage and / or lubrication needed at this point.
  • a further advantageous possibility provides that an electrical conductor of the electrical supply device within the connection section are electrically connected by contact fingers to the electrical connection of the pump device.
  • a contacting of the electrical conductors of the electrical supply device can be achieved by attaching the connection portion.
  • a particularly favorable solution provides that the electrical supply device runs within a tube which runs inside the hollow shaft. As a result, an electrical conductor of the electrical supply device is guided through the tube, so that no desired contact, for example with the hollow shaft, can arise.
  • the electrical conductors of the electrical supply device do not have to have special mechanical stability of their own, so that the electrical properties of - -
  • Shafts of the electrical supply device and electrical conductors may be in the foreground.
  • a particularly advantageous solution provides that the electrical supply device is guided through the center of the drive shaft and that the drive shaft has a hollow shaft.
  • the advantage of this solution is that the pressure that can be generated by an impeller increases quadratically with the diameter of the impeller so that increasing the diameter of the drive shaft causes less loss than the loss caused by reducing the diameter of the impeller Impeller would cause.
  • Another advantage is that increasing the diameter of the drive shaft causes less reduction in engine output than reducing the outside diameter of an electric motor.
  • the object is achieved in the above-mentioned pumping device according to the invention by at least one second pumping element for generating a pressure difference, wherein the first pumping element and the second pumping element are arranged and configured to each other such that an axial thrust in the generation of the pressure difference on the first Pumping element acts, opposite to an axial thrust, which acts on the generation of the pressure difference on the second pumping element.
  • a particularly advantageous possibility provides that the first pumping element has a first impeller with a suction mouth and that the second pumping element has a second impeller with a suction mouth and that the suction mouth of the first impeller are facing away from each other and in particular are arranged in opposite directions or point.
  • first pumping element and the second pumping element are arranged coaxially with each other, generate the oppositely directed axial forces acting on the first pumping element and on the second pumping element, no torque, which is advantageous for the compensation of the axial forces.
  • a favorable possibility provides that the second pumping element is formed and arranged substantially mirror-symmetrically to the first pumping element. Thereby, the axial forces acting on the first pumping element and the axial forces acting on the second pumping element are substantially equal, whereby the axial forces can be almost completely compensated.
  • An advantageous possibility provides that the first pumping element and the second pumping element are fixed against each other at least in the axial direction. By this fixation in the axial direction, the axial forces acting on the first pumping element and on the second pumping element are coupled together, whereby these forces can cancel.
  • a particularly favorable possibility provides an inner sleeve, on which the first pumping element and the second pumping element are rotationally fixed and held in the axial direction.
  • both the rotation of the first pumping element and of the second pumping element are coupled, as well as the axial forces acting on the first pumping element and on the second pumping element. Due to the coupling of the rotation, the axial forces which are also applied to the first pump - - Lement act and the axial forces acting on the second pumping element, substantially the same size, so that cancel the axial forces almost completely.
  • a favorable solution provides that the first pumping element is arranged in a first pressure generating area, which has an axial suction opening, and that the second pumping element is arranged in a second pressure generating area, which has an axial suction opening, and that the axial suction opening of the first pressure generating area and the axial suction opening of the second pressure generating area are directed in opposite directions.
  • the location of the axial suction ports relative to the pumping elements determines the direction of the axial forces acting on the pumping element.
  • a particularly favorable solution provides that the first pressure generating area and the second pressure generating area are arranged adjacent to one another and that the axial suction openings are arranged on opposite sides of the pressure generating areas.
  • the two pumping elements are flowed through the same.
  • a space-saving arrangement of the first pressure generating area and the second pressure generating area is achieved.
  • first pressure generating area is limited in the radial direction to the outside by a first radial partition, which at least one outlet opening of the first pressure generating area - - having.
  • fluid to be pumped that has flowed through the pressure generating area may leave it through the outlet openings in the radial direction, so that no further axial forces are generated on the pumping element by the outflow of the pumping fluid from the pressure generating area.
  • a particularly advantageous solution provides that the at least one outlet opening establishes a fluid-effective connection from the first pressure generating area to a fluid passage, which fluidly connects the at least one outlet opening of the first pressure generating area with the axial suction opening of the second pressure generating area.
  • a hydraulic series connection of the first pumping element with the second pumping element can take place, whereby the achievable pressure difference of the pumping device is given by the achievable pressure differences of the individual pumping elements.
  • a particularly advantageous solution provides that at least one first fluid channel extends starting from the at least one outlet opening of the first pressure generating area up to a return region. The first fluid channel thus forms a first part of the fluid passage.
  • the expansion of the first fluid channel is limited in the circumferential direction and is limited in the radial outward direction by a cylindrical outer wall of the pumping device and inwardly by the first radial partition wall and a second radial partition wall.
  • first fluid channel is limited in the circumferential direction, it is possible to arrange further fluid channels offset in the circumferential direction, which are not directly connected fluidly effective with the first fluid channel. This opens up a greater freedom of design with regard to the arrangement of individual regions in the pump device.
  • a solution which is advantageous for an equal effect of the first pumping element and the second pumping element provides that the second pressure generating device Area is limited in the radial direction to the outside by a second radial partition, which has at least one outlet opening of the second pressure generating area.
  • a further favorable solution provides that at least one second fluid duct extends from the at least one outlet opening of the second pressure generating area to a return and outlet area.
  • the fluid to be pumped, after having passed through the second pressure generating area, can be led to an outlet port.
  • the at least one second fluid channel is limited in the circumferential direction, and the at least one second fluid channel is arranged offset in the circumferential direction to the at least one first fluid channel.
  • each of the first fluid channel and the second fluid channel may independently extend in a region radially outside of the first pressure generating portion and the second pressure generating portion.
  • Another particularly advantageous solution provides a (uniform) pump cartridge in which the at least one first pumping element and the at least one second pumping element are arranged.
  • the combination of the first pumping element and the second pumping element in a single pumping cartridge makes it possible to produce a unit in which the on the
  • the pumping cartridge has at least a first section, in which a first pressure generating area is arranged, has a second section, in which a second pressure generating area is arranged, has a third section, in which a return area is arranged and a fourth portion in which a return and outlet region is arranged.
  • the invention is also based on the object to provide a pumping device of the type mentioned, in which the assembly of the
  • the drive shaft is a hollow shaft or that the at least two pumping elements are rotatably connected in a first region of the drive shaft to the drive shaft and that the drive shaft in a second region of the drive shaft which is different from the first area is stored.
  • the use of a hollow shaft leads to a higher rigidity of the drive shaft, whereby it no longer has to be supported between the individual pumping elements, so that the bearing of the drive shaft outside the pumping elements is sufficient.
  • a favorable solution provides that the hollow shaft is mounted in two places. In this way, the drive shaft can be sufficiently stored with a small number of bearings, so that both the assembly is easier and costs for the individual bearings can be saved.
  • the hollow shaft may be integrally formed, which further increases the bending stiffness of the drive shaft.
  • a particularly favorable solution provides that the hollow shaft is mounted in the connection section of the pump device.
  • the bearing of the hollow shaft obstructs the flow of fluid within the pumping device less than - - If the camp would be located between two pumping elements.
  • the hollow shaft is mounted in the vicinity of the end of the hollow shaft, whereby the bearing can absorb torques acting transversely to the axis of rotation of the hollow shaft to the hollow shaft, better.
  • the hollow shaft is mounted in the drive section of the pump device.
  • the support of the drive shaft is arranged in a region of the pumping device through which the fluid to be pumped does not flow.
  • the bearing of the hollow shaft in the region of the end of the hollow shaft is also arranged here, so that the recording of torques, which create transversely to the axis of rotation of the hollow shaft, can be better absorbed.
  • the pumping device has a first bearing device which supports the hollow shaft, and a fixing and bearing device (second bearing device) which supports the hollow shaft.
  • a favorable solution provides that the first storage device has at least one radial ring bearing, through which the hollow shaft is mounted. This radial bearing prevents tilting of the hollow shaft.
  • Another particularly favorable solution provides that the at least one first radial ring bearing is arranged within an electric motor of the drive.
  • the hollow shaft can serve both as the drive shaft of the pump device and as the drive shaft of the electric motor.
  • the first radial ring bearing acts as a bearing for the pumping device and an electric motor of the drive.
  • the fixing and mounting device has at least one radial ring bearing, through which the hollow shaft is mounted.
  • the at least one radial annular bearing of the fixing and mounting device is located within a - - Nes support portion of the fixing and storage device is located in the connection portion of the pumping device, since in this way the radial ring bearing is mounted together with the support portion of the fixing and storage device.
  • the radial ring bearing can not be inserted too early, ie between the pumping elements.
  • the drive has a motor whose speed is independent of a mains frequency.
  • the speed of the drive can be greater than the mains frequency of, for example, 50 hertz. This is advantageous because the achievable delivery height per impeller depends both on the diameter of the impeller and on the speed of the impeller. In this way, therefore, the number of required impellers can be reduced.
  • the drive has an electronically commutated synchronous motor.
  • Such electric motors have a high efficiency, are easy to control and allow high speeds.
  • the rotor of the electric motor of the drive is held by a connecting portion on the hollow shaft. It is particularly advantageous that the rotor of the electric motor of the drive is held only on the hollow shaft, since thus no separate bearing of the rotor is necessary and this is guided by the hollow shaft.
  • Pumping device must be operated at higher speeds with smaller diameters (in comparison with a pump device with a larger one)
  • an advantageous solution provides that the drive shaft is supported only by two radial bearings, which is arranged outside a region of the vanes.
  • a particularly favorable possibility provides that the drive has a high speed, so that the number of impellers can be reduced, so that the drive shaft does not require support between the impellers.
  • Another particularly advantageous possibility provides that the drive shaft from the drive to the impellers is formed integrally, so that the two bearings are sufficient to support the hollow shaft.
  • a further advantageous possibility provides a hollow shaft, which has a higher flexural rigidity than conventional shafts.
  • the drive shaft is or comprises a hollow shaft - -
  • the pumping device has an armature for receiving axial forces, which extends through the hollow shaft.
  • an outer wall of the pumping device must transmit no or small forces, so that no external thread in the outer wall are required for power transmission, which would have a large diameter and would be needed for the special tool for assembly.
  • flare can be avoided, which would have to transmit large forces and thus would be expensive to produce.
  • Pumping forces is formed, which arise during pressure generation during operation.
  • the magnitude of the pumping forces is essentially given by the generated pressure difference multiplied by the cross-sectional area of the pumping device.
  • the central armature is designed to absorb pumping forces which occur when pressure is generated, the outer wall does not have to transmit any or fewer forces.
  • the armature is arranged coaxially to a rotational axis of a pumping element, wherein the pumping element serves to generate a pressure difference. In this way, bending moments acting on the anchor can be reduced. - -
  • a rod-shaped anchor offers the highest tensile stability for a given maximum diameter.
  • the armature extends from a connection section starting through the pumping element and through an electric motor of the drive.
  • the pumping device is held at the connecting portion, in particular by a hose or a pipe.
  • the armature extends from the terminal portion, starting by the pumping element and by the electric motor, it can absorb forces and transmitted to the terminal portion. The forces arise in areas on the pumping device in which the pumping element and / or the electric motor are arranged.
  • a pumping element comprises or is an impeller. If an impeller is a pumping element that operates on the principle of flow pumps, no valves or flaps are needed.
  • the effectiveness of an impeller depends on the distance to the axis of rotation, so that the effect of the central arrangement of the armature and thus the leadership of the forces comes to full advantage.
  • the armature force-effectively connects the drive unit with a connection section is understood to mean that forces, in particular axial tensile forces are transferable. Due to the fact that the armature connects the drive unit to the connection section in a force-effective manner, the pump device is held together and
  • a particularly advantageous possibility provides that the armature is held by a detachable connection to a connection section.
  • a disassembly of the pumping device is possible, which is advantageous for example in repairs of the pumping device.
  • a favorable solution for holding the pumping device provides that the detachable connection of the armature at the connection portion can absorb and absorb forces in at least one direction.
  • a further favorable solution provides that a connection section comprises a fixing and storage device with a carrier section and that the armature extends through the carrier section and that the armature has a securing section which projects beyond the carrier section. In this way, the support portion can be engaged behind to allow a force-effective connection.
  • An advantageous solution provides that the securing portion of the armature has a thread. Through a thread a simple and stable connection is possible.
  • fastener with which the securing portion is held.
  • Possible fasteners are based in particular on frictional connection, material connection, positive connection or the like.
  • fasteners include bolted, screwed or glued joints. This is advantageous since the fastening element engages behind the carrier section, so that the armature can not be pulled out of the carrier section. This results in a force-effective connection, at least for tensile forces.
  • the fastening element has or is a nut, in particular a retaining nut, which can be screwed and / or screwed onto the securing section of the anchor.
  • a nut is easy to assemble and on the other hand, the diameter of the nut is larger than the diameter of the securing portion, so that a shoulder forms, which can engage behind the carrier portion and / or engages behind.
  • the drive unit comprises a drive section which has a base section to which the drive unit - - ker is held. By the base section forces can be directed to the anchor.
  • the anchor is held, for example, by positive engagement, material connection or the like to the base portion.
  • the invention is further based on the object to provide a pump device which has an optimized cooling of the drive.
  • the electric motor is arranged in a filled with a coolant region comprising a coolant circuit, that the coolant circuit has at least one branch extending at least partially along the outer wall of the pumping device, and a coolant circulation in the coolant circuit is driven during operation of the electric motor.
  • the coolant can deliver heat to the environment of the pump device. This is very effective in particular with a pumping device which is immersed in the fluid to be pumped, since the heat can thus be released very well via the outer wall of the pumping device to the fluid to be pumped. It is advantageous if the electric motor has a rotor and if the coolant circulation in the coolant circuit is driven by the rotation of the rotor. This can be achieved without additional coolant pump effective cooling.
  • the coolant circuit has at least one branch which extends at least partially along the windings of the motor.
  • the coolant can effectively absorb the waste heat generated in the electric motor.
  • the electric motor has a rotor (internal rotor or external rotor), which has at least one bore - - Which causes a fluid-effective connection from an interior of the electric motor to an exterior of the electric motor.
  • Electric motors with a bell-shaped rotor are so-called external rotor motors, which have a particularly high power density and are particularly difficult to cool due to the bell-shaped rotor.
  • the coolant can transport the waste heat of the electric motor through the rotor and thus achieve effective cooling of the electric motor.
  • the pumping device has at least one radial annular bearing which is arranged within the area filled with coolant. In this way, the radial ring bearing can be cooled and lubricated by the coolant.
  • a further advantageous solution provides that the coolant circuit has at least one branch which extends at least in sections along the at least one radial annular bearing. As a result, a circulation of the coolant is achieved along the radial annular bearing, whereby a particularly good lubrication and cooling of the radial annular bearing is achieved.
  • the pumping device has at least two radial annular bearings and that at least partially along the at least two radial annular bearings each extend at least one branch of the coolant circuit. In this way it can be achieved that the coolant circulates along both radial ring bearings, whereby a good cooling and lubrication of the two radial ring bearings can be achieved.
  • the pumping device has a drive shaft for torque transmission between the drive and the at least one pumping element for generating a pressure difference, which is designed as a hollow shaft or has a hollow shaft. Hollow shafts have the same weight to a higher rigidity than shafts, which are solid. - -
  • the coolant circuit has at least one branch which extends at least in sections within the hollow shaft.
  • the coolant within the pumping device can also be used outside the drive, for example for cooling or for lubrication.
  • the hollow shaft has at least one bore, which causes a fluid-effective connection from an interior of the hollow shaft to an exterior of the hollow shaft. Through this hole, the coolant circuit can be targeted directed to the places where cooling or lubrication is needed.
  • a particularly advantageous possibility provides that at least one bore is arranged in the hollow shaft within the electric motor. In this way, the circulation of the coolant within the electric motor can be adjusted so that the areas where most of the waste heat is generated can be sufficiently cooled.
  • a favorable solution provides that the electric motor has a rotor with a connecting portion, with which the rotor is held on the hollow shaft, that the connecting portion has at least one bore and that the hollow shaft has at least one bore which is aligned with the at least one bore in is arranged the connecting portion.
  • the coolant can pass from an interior of the hollow shaft through the connecting section into a region outside the rotor of the electric motor and be conducted there, for example, to the outer wall of the pump device.
  • Another favorable solution provides that at least one bore in the hollow shaft is arranged within a first radial annular bearing, which is arranged within the drive. Characterized in that the at least one bore is disposed within the first radial annular bearing, the coolant can be fed directly to this radial ring bearing, whereby this can be lubricated by the coolant (with lubricating function).
  • the pumping device has at least a second radial annular bearing, with which the hollow shaft is mounted against a pipe arranged in the hollow shaft and that the tube has at least one bore which connects from an interior of the tube causes an exterior of the tube. Due to the fact that the second radial annular bearing supports the hollow shaft against the tube, which is arranged inside the hollow shaft, the second radial annular bearing can be arranged in a region filled with the coolant and at the same time be arranged outside the drive. Characterized in that the tube has at least one bore which causes a connection from an interior of the tube to an exterior of the tube, the coolant through the tube within the
  • the tube has at least one bore which, viewed from the drive, is arranged behind the second annular bearing, since in this way the coolant must flow past the radial annular bearing and thus the can cool and lubricate second radial ring bearings.
  • the pumping device is designed as a borehole pump or comprises a borehole pump. Since a wellbore pump is intended for use in a wellbore, the pumping device emerges during operation within the fluid to be pumped, whereby the cooling via the outer wall of the pumping device is particularly effective. In addition, the good cooling in a borehole pump is particularly advantageous because of the limited space within the well, the removal of waste heat from the drive is particularly problematic.
  • bearings with which the drive shaft is mounted can in principle come into contact with the fluid to be pumped.
  • Fluid to be pumped may contain particles, which can lead to increased wear on the bearings and drive shaft.
  • the invention has for its object to reduce the load on the bearings in the pump device mentioned above.
  • the electric motor is arranged in a filled with a coolant region comprising a coolant circuit, wherein a coolant circulation is driven during operation of the electric motor, that the drive shaft is formed as a hollow shaft or has a hollow shaft and that the pumping device has at least one radial annular bearing on which the drive shaft is mounted and which is arranged within the region filled with coolant.
  • the drive shaft is formed as a hollow shaft or comprises a hollow shaft, the drive shaft has a high rigidity, whereby the number of bearings can be reduced.
  • the pumping device has at least one radial annular bearing with which the drive shaft is mounted and which is arranged within the area filled with coolant, the radial annular bearing does not come into contact with the fluid to be pumped, so that the wear of the radial annular bearing is reduced can be.
  • the coolant may contain ingredients that may serve for lubrication.
  • the coolant may contain ingredients that may serve for lubrication.
  • the coolant circuit has at least one branch which extends at least in sections along the radial annular bearing. In this way, the coolant is also circulated on the radial ring bearing, so that a good lubrication and good cooling of the radial ring bearing is ensured.
  • the pumping device has at least two radial annular bearings and that extends at least partially along the at least two radial ring bearings in each case at least one branch of the coolant circuit.
  • the drive shaft With two radial ring bearings, the drive shaft can be stored well. Because at least one branch of the coolant circuit extends to each of the at least two radial ring bearings, these radial ring bearings can be sufficiently lubricated and cooled.
  • the coolant circuit has at least one branch which extends at least in sections within the hollow shaft.
  • a branch of the coolant circuit extends within the hollow shaft, the coolant can be selectively directed within the pumping device.
  • the hollow shaft has at least one bore, which causes a fluid-effective connection from an interior of the hollow shaft to an exterior of the hollow shaft.
  • the coolant can be directed at a specific point into the hollow shaft or out of the hollow shaft in a targeted manner in order to distribute the coolant as required.
  • at least one bore is arranged in the hollow shaft within a first radial annular bearing, which is arranged within the at least one drive.
  • the radial ring bearing which is arranged within the at least one drive, be sufficiently supplied with coolant for lubrication and cooling.
  • the pumping device has at least a second radial annular bearing, on which the hollow shaft is mounted against a tube arranged in the hollow shaft and that the tube has at least two holes, which connects from an interior of the tube to an exterior of the Effect tube.
  • the bearing is within the hollow shaft, whereby the second radial ring bearing in one with the coolant - - filled area is arranged.
  • the tube disposed within the hollow shaft may be used to direct the coolant within the pumping device.
  • Another favorable solution provides that the second radial ring bearing is arranged behind the pumping element when viewed from the drive. In this way, a second bearing point is achieved for the hollow shaft, which is spaced from the first bearing point, so that the shaft is sufficiently secured against tilting.
  • a particularly favorable solution provides that the tube has at least two holes which, viewed from the drive, are arranged behind the second radial ring bearing and / or within the second radial ring bearing. In this way it can be ensured that the second radial ring bearing is sufficiently supplied with coolant for cooling and lubrication.
  • An advantageous solution provides that the coolant circuit has a branch which extends at least in sections within the tube. In this way, the coolant circuit can be closed because, for example, the coolant within the tube flows away from the drive in the direction of a connection section and outside the tube but flows back inside the hollow shaft.
  • a further advantageous solution provides that the coolant circuit has at least one branch which extends at least in sections along the outer wall of the pump device. In this way, the coolant can effectively deliver waste heat to the environment of the pumping device.
  • the electric motor has a rotor with a connecting portion, with which the rotor is held on the hollow shaft, that the connecting portion has at least one bore and that the hollow shaft has at least one bore, which is aligned with the at least one bore is arranged in the connection section. In this way, a branch of the refrigerant circuit outside - - Are guided along the rotor of the motor, whereby it can extend to and along the outer wall of the pumping device.
  • the electric motor has an internal rotor or external rotor as a rotor, which has at least one bore, which causes a fluid-effective connection from an interior of the electric motor to an exterior of the electric motor.
  • the coolant which has absorbed waste heat in the electric motor, can transport the waste heat from the electric motor and thus ensure effective cooling of the electric motor.
  • the electric motor has a rotor and if the coolant circulation in the coolant circuit is driven by the rotation of the rotor. As a result, effective cooling can be achieved without additional coolant pumps.
  • the coolant circuit has at least one branch which extends at least partially along the windings of the electric motor, since the largest part of the waste heat is generated in the windings of the electric motor.
  • the pumping device is designed as a borehole pump or has a borehole pump.
  • the advantages of the invention can be exploited particularly well, since due to the cramped conditions within the well, the cooling problem is significant and the fluid to be pumped often contains particles such as sand.
  • the coolant comprises water and glycol.
  • a mixture of water and glycol has proven itself as a combined coolant and lubricant.
  • kits for a pump device for conveying fluid comprising at least one drive unit with a drive and at least one receiving area on which at least two pumping cartridges can be hydraulically positioned in series, one set Pump cartridges, each with a housing with a first
  • Connection side which has a suction port, and with a second
  • Terminal side which has an outlet opening, wherein in the set of pumping cartridges at least two of the pumping cartridges have different pump powers.
  • individual pump cartridges can be designed for different flow rates, which then require weaker or stronger drive units.
  • the achievable pressure can be varied, for example, by the rotational speed of the drive unit.
  • One measure of the pumping capacity is a delivery height as the usable mechanical work transferred from a pump to a delivery fluid.
  • the pumping power can also be zero.
  • a pumping cartridge comprises at least one pumping element arranged in the housing for generating a pressure difference between the suction opening and the outlet opening.
  • at least one pump cartridge from the set of pumping cartridges has a pumping power that is different from zero.
  • the at least one pumping element comprises an impeller.
  • impellers By means of impellers, high pump powers can be generated in a small space.
  • a particularly advantageous possibility provides that in the set of pump cartridges at least two pumping cartridges have different pump powers, that a distance between a first wall of the impeller and a second wall of the impeller is different in size, between which the fluid to be pumped in rotation is offset.
  • the active volume of the pump cartridge can be adjusted by rotating the fluid to be pumped so that the flow rate and the required torque can be varied.
  • the set of pump cartridges comprises an empty cartridge, which has no pumping element and no pumping power.
  • the achievable pressure can be reduced by the pressure achieved by the pump cartridge, and accordingly the required drive power can be reduced.
  • the pump power can be adapted to the requirements of most applications by a relatively small number of different drive units and pump cartridges, each of which can be freely exchanged with each other.
  • the drive unit has a drive shaft which extends through the receiving area and that in the set of pumping cartridges at least one of the pumping cartridges has an inner sleeve which is slidable over the drive shaft of the drive unit. This simplifies the assembly of the pumping device, since in such an embodiment the pumping cartridges can be positioned on the receiving region of the drive unit.
  • a particularly advantageous solution provides that the inner sleeve is held against rotation on the drive shaft.
  • the drive power of the drive unit can be transmitted to the pump cartridge via the drive shaft.
  • a favorable solution provides that the inner sleeve is held by positive engagement with the drive shaft.
  • a particularly advantageous solution provides that the inner sleeve extends over the entire height of the respective pump cartridge.
  • the inner sleeve of a further pumping cartridge can be supported on the inner sleeve of the first pumping cartridge so that the mobility of the inner sleeve is limited in the axial direction when the pumping device is mounted.
  • the set of pumping cartridges comprises at least one pumping cartridge, which has a pumping element which is rotationally fixed to the inner sleeve of the pumping cartridge and firmly held in the axial direction.
  • the pump element is set in rotation by the rotation of the drive shaft, and fixed in the axial direction by the inner sleeve.
  • the pumping element generates a pressure difference between the suction opening and the outlet opening of the pumping cartridge when it is set in rotation by the drive shaft. The pressure difference between the suction opening and the outlet opening causes a flow of the fluid to be delivered, so that the fluid can be conveyed from the place of use of the pumping device to a destination.
  • a further advantageous solution provides that the housing of at least one pump cartridge from the set of pumping cartridges has an outer wall which, when the pumping cartridge is positioned in the drive unit, rests against an outer wall of the pumping device. In this way, the space available can be optimally utilized. Furthermore, this fixes the pump cartridge in the radial direction within the pump device.
  • a particularly favorable solution provides that the first connection side and the second connection side of the pumping cartridges from the set of pumping cartridges are designed to be complementary to each other. This allows that - -
  • the first connection side has a sealing surface and if the second connection side has a sealing surface which is arranged in the axial direction in alignment with the sealing surface of the first connection side.
  • the sealing surfaces of the second connection side of a first pump cartridge and the sealing surface of the first connection side of a second pump cartridge when the first pumping cartridge and the second pumping cartridge are positioned in a drive unit, seal the transition between the first pumping cartridge and the second pumping cartridge.
  • a further particularly advantageous solution provides that the first connection side of at least one of the pump cartridges from the set of pumping cartridges has an inlet-side bottom which has a central opening, wherein the suction opening is annular in the central opening, and the second connection side is at least one of the pumping cartridges from the set of pumping cartridges has an opposite outlet-side bottom which has a central opening, wherein in the central opening the outlet opening is annularly formed.
  • Another particularly advantageous solution provides that the outlet opening of a first pumping cartridge from the set of pumping cartridges, which is positioned on the receiving area, is arranged flush with the suction opening of a second pumping cartridge from the set of pumping cartridges, which is positioned on the receiving area.
  • the at least one drive unit has a suction section, which is arranged between the drive and the at least one receiving area and in which an outer wall of the pumping device has a plurality of suction holes, through which fluids to be pumped into the - -
  • the drive can be arranged so that the drive is located in the area of the pumping device through which the fluid to be pumped flows, so that the cross section is available so that the fluid to be pumped is not restricted by the drive.
  • a further particularly favorable solution provides that the receiving region of the at least one drive unit has a cartridge connection, which is designed to be complementary to the first connection side of the pumping cartridges from the set of pumping cartridges.
  • a pump cartridge from the set of pump cartridges can be positioned in the drive unit without the need for additional connecting elements and / or adapter elements.
  • a further particularly volteilhafte solution provides that the kit has at least two drive units, which have different drive powers. This increases the number of possible combinations of pump cartridges and drive units, so the spectrum of
  • the at least two drive units have different motors.
  • the motors essentially determine the drive power that the drive unit can provide.
  • the motors can differ in particular in the achievable speed and in the achievable torque and thus influence achievable pressure and achievable delivery rates.
  • Another particularly advantageous solution provides that in the receiving areas of at least two drive units, a different number of pump cartridges from the set of pump cartridges are positioned. In this way, in particular the achievable pressure of the pumping device can be varied.
  • the above object is achieved according to the invention by a method for producing a pumping device from a kit in particular a kit according to the above explanations, wherein a required pumping power of the pumping device is determined, to achieve the pumping power necessary pumping cartridges are selected from a set of pumping cartridges and a Drive unit is selected, which has a necessary for driving the pump cartridges drive power.
  • An advantageous variant provides that the selection of the pump cartridges from the set of pumping cartridges after the achievable with the pump cartridges flow rate. For example, pumping cartridges are selected which have the smallest flow rate, which exceeds the required flow rate. This is advantageous because the pump cartridges can work very efficiently in this way.
  • a favorable variant provides that the selection of the pump cartridges from the set of pump cartridges after the achievable with the pump cartridges head.
  • Several identical pump cartridges can be selected or pump cartridges which differ in the delivery height or the achievable pressure, in particular a combination of a pump cartridge and an empty cartridge is possible. In this way, for the required flow rate an optimized combination of pump cartridges - - are selected to achieve the required flow rate, allowing the pump cartridges to operate efficiently.
  • a particularly advantageous variant provides that the selection of the drive unit takes place after the speed required for the required delivery height.
  • the pressure generation of the pump cartridges is speed-dependent, so that the speed of the drive unit, the head and the pressure can be adjusted.
  • a favorable possibility provides that the selection of the drive unit takes place after the torque required for the required flow rate.
  • the torque required to drive the pump cartridges is usually dependent on the flow rate.
  • a drive unit can be selected, which is optimized for the required torque.
  • An advantageous possibility provides that, after the selection of the pumping cartridges and the drive unit, the pumping cartridges are positioned on a receiving area of the drive unit.
  • the positioning of the pumping cartridges on the receiving area of the drive unit takes place in that the pumping cartridge is threaded over a drive shaft of the drive unit and pushed along this to a cartridge connection of the drive unit. In this way, the pump cartridge is guided during positioning, so that a correct positioning is facilitated.
  • a particularly favorable possibility provides that when positioning the pump cartridges or the empty cartridges no further elements must be inserted into the drive unit. This is advantageous because a possible source of error in the assembly of the pumping device is eliminated.
  • a particularly advantageous possibility provides that, after the positioning of the pumping cartridges on the receiving area of the drive unit, a closing section is placed on the drive unit so that the connecting section encloses the pumping cartridges in the drive unit.
  • a closing section is placed on the drive unit so that the connecting section encloses the pumping cartridges in the drive unit.
  • connection section is fixed to the drive unit by at least one fastening element.
  • the pumping device is held together because the connecting portion encloses the pumping cartridges in the receiving area of the drive unit and the connecting portion itself is fixed to the drive unit.
  • the at least one fastening element can be based, for example, on fabric seams by gluing or welding, frictional engagement, by a screw connection or other form fit or the like.
  • the pump cartridges have all the necessary elements such as seals and bearings. This solution is advantageous because it is almost impossible to forget a component during assembly, since only the pump cartridges must be used.
  • the pumping cartridges include all the elements needed for a pumping stage or a group of pumping stages, so that no loose elements are needed.
  • the pump cartridges have an installation safety device.
  • the installation of the mounting device ensures that the pump cartridges can not be installed incorrectly, for example, on the head.
  • An installation safety device has, for example, an asymmetrical arrangement of grooves in the drive shaft.
  • the solution according to the invention makes it possible to configure / assemble the pump devices for use in a central warehouse or distribution center, at a dealer or directly at the place of use. As a result, the required storage space at the dealer can be significantly reduced, which is needed to cover the full range of requirements.
  • FIG. 1 is a perspective view of a first embodiment of a
  • FIG. 2 is a sectional view of the pumping device according to Figure 1 in the
  • FIG. 3 shows a detail enlargement of the region B according to FIG. 2;
  • Figure 4 is a partial perspective sectional view of the area B
  • FIG. 5 shows a detail enlargement of the sectional representation from FIG. 2 of the pumping device with a drive section, a suction section and a pump section;
  • FIG. 6 shows a perspective partial sectional illustration of a pump section of the pumping device according to FIG.
  • FIG. 20 a detail enlargement of the region F of the sectional view according to FIG. 18.
  • FIG. 1 An exemplary embodiment of a pump device 10 (FIG. 1) has a head section 12, a drive section 14, a pump section 16 and a connection section 18, which follow one another in an axial direction 19.
  • the pumping device 10 has an outer wall 13 extending from the head portion 12 to the terminal portion 18.
  • the outer wall 13 is at least partially substantially cylindrical and / or arranged coaxially to a main axis 11 of the pumping device 10.
  • the head section 12 has a cross-section 20 which decreases in size from a connecting end 22 to a vertex 24 located opposite the connecting end 22, in particular monotone and rotationally symmetrical to the main axis 11.
  • the cross section 20 has a curved contour, for example a circular contour.
  • the taper of the cross-section 20 is monotone and increases in the vicinity of the apex 24, so that an edge-free rounded shape 26 of the head portion 12 is present.
  • the head portion 12 has one or more, for example, eight, reinforcing ribs 28 extending inwardly from an outer wall 30 (which is particularly part of the outer wall 30) of the head portion 12 to an inner (hollow) cylinder 32. These increase the mechanical rigidity of the head portion 12.
  • the head portion 12 in the region of the connecting end 22 at least one connecting element 34 and four connecting elements 34, for example, with which the head portion 12 is held on the drive portion 14. - -
  • the head section 12 may be held for example by screwing, bonding, riveting or flanging on the drive section 14.
  • the head portion 12 is held on a base member 36 of the drive portion 14.
  • the base element 36 has counter elements 38 for the connection elements 34 of the head section 12.
  • the base element 36 has an outer, in particular cylinder wall-shaped, outer section 40 extending in the axial direction 19.
  • the outer portion 40 has on its side facing away from the head portion 12 a tapered portion 41, wherein at the transition to the tapered portion 41 on the inside of the outer portion 40, a shoulder 43 is formed (Figure 5).
  • the outer portion 40 merges, on its side facing the head portion 12, into a base portion 42 that extends inwardly from the outer portion 40 to a central opening 44.
  • the central opening 44 lies on the main axis 11.
  • a region 46 of the base element 36 located at the central opening 44 lies closer to the head section 12 in the axial direction 19 than a region 48 of the base section 42 adjoining the outer section 40.
  • the base portion 42 has, for example, the shape of a blunt cone portion.
  • a holding device 50 is arranged, through which an armature 52, in particular a central armature 52, is held, which extends from the drive section 14 through the pump section 16 into the connection section 18. Further details about the central anchor 52 will be explained below.
  • the holding device 50 is, for example, cylindrically shaped, and extends from the region 46, adjoining the central opening 44, of the base section 42, starting in the axial direction 19 away from the head section 12. - -
  • the holding device 50 is designed for connection to the armature 52.
  • one or more electrical conductors 56 are guided, which are for example part of an electrical supply device 58 or an electrical connection line 60 for a drive 62 of the pump device 10.
  • the electrical conductors 56 are associated with a guide device 64 which encloses the electrical conductors 56 at least in sections.
  • the electrical conductors 56 of the electrical supply device 58 and the electrical connection line 60 are connected to a motor control 66 (FIG. 3).
  • the motor controller 66 is disposed adjacent the base member 36 between the base member 36 and the reinforcing ribs 28 in a transition region 68 between the drive portion 14 and the head portion 12.
  • the electrical connection lines 60 connect the motor control 66 with windings 70 of at least one electric motor 72 of the drive 62.
  • the engine control 66 has, for example, a motor controller for an electronically commutated synchronous motor.
  • the electric motor 72 has, for example, an internal stator 74 with the windings 70 and a rotor 76.
  • the stator 74 of the motor 72 has a central through-opening 94, through which the central armature 52, the electrical supply device 58 and a hollow shaft 92 are guided.
  • the stator 74 is disposed on a motor base member 80 and held rotatably thereto.
  • the engine base member 80 has a flat base portion 82.
  • the base section 82 is in particular of annular design and has an opening 84 coaxial with the main axis 11.
  • the base section 82 merges into a first, in particular cylinder-wall-shaped, outer wall 86, which extends in the axial direction 19 in FIG - -
  • the second outer wall 90 is non-rotatably held on the base element 36, for example by material connection or positive connection.
  • the pump device 10 has a first bearing device 95, through which the hollow shaft 92 is rotatably mounted.
  • the first bearing device 95 has, for example, a radial ring bearing 36, which is arranged within a central opening 94 of the stator 74 and which supports the hollow shaft 92.
  • the radial ring bearing 96 is disposed adjacent to the engine base member 80.
  • the radial ring bearing 96 is for example a sliding bearing or a rolling bearing.
  • the electric motor 72 has the rotor 76 provided with permanent magnets. This is designed for example as an external rotor and in particular has a bell shape.
  • the permanent magnets are, for example, ferrite magnets or rare-earth magnets.
  • the rotor 76 has an example zyiinderwandförmigen support portion 98, on the inside of which sector-like permanent magnets 100 are arranged.
  • the support portion 98 surrounds the stator 74. - -
  • the carrier section 98 merges on an end facing away from the head section 12 into an annular base section 102, which extends from the carrier section 98 to a connecting section 104.
  • the connecting section 104 extends from the annular base section 102 in the axial direction 19 in the direction of the connecting section 18.
  • the connecting section 104 has a cylinder wall.
  • the rotor 76 On an inner side 106 of the connecting portion 104, the rotor 76 is held on the hollow shaft 92 and fixed thereto. The rotor 76 is rotationally fixed and connected in the axial direction 19 fixed to the hollow shaft 92.
  • the drive section 14 comprises a closing element 108 (for example, FIGS. 4, 5), which closes off the drive section 14 in a fluid-tight manner.
  • the closing element 108 has an outer wall 110, which is in particular cylindrical-wall-shaped, and rests against the outer wall 13 of the pump device 10.
  • the outer wall 110 of the terminating element 108 on its side facing away from the electric motor 72, merges into a cover section 112 which extends radially inwards from the outer wall 110 and away from the electric motor 72 in the axial direction 19, the cover section 112 being in a (pointed) manner. Angle to the main axis 11 is located.
  • the cover section 112 has a central opening 114 on the main axis 11, through which the central armature 52, the electrical supply device 58 and the hollow shaft 92 extend.
  • the closing element 108 has a cylinder-wall-shaped seal carrier section 116, on which a radial seal 118 is arranged or formed.
  • the radial seal 118 seals the transition between the end element 108 and the hollow shaft 92.
  • the radial seal 118 is designed such that a rotation of the hollow shaft 92 (about a rotation axis coaxial with the main axis 11) is possible. - -
  • the closing element 108 creates a sealed region 127 (FIG. 5) which is sealed in a fluid-tight manner with respect to flowing conveying fluid (indicated in FIG. 5 by the reference numeral 126).
  • an intake section 120 extends as far as an axial seal carrier 122.
  • the outer wall 13 of the pump device 10 has a plurality of suction openings 124. Through the suction openings 124 can be sucked fluid to be pumped (delivery fluid) 126 through the pumping device 10.
  • the Axialdichtungst 122 has a particular cylindrical outer wall 128 which rests against the outer wall 13 of the pumping device 10 and is held thereon.
  • the outer wall 128 of the Axialdichtungsts 122 may be maintained, for example, by material bond or positive connection to the outer wall 13 of the pump device 10.
  • the outer wall 128 of the axial seal carrier 122 merges at its side facing the connection section 18 into a shoulder 132 forming a sealing surface 130 (FIG. 8).
  • the shoulder 132 merges into a securing section 134, which extends from the shoulder 132 in the axial direction 19 in the direction of the connecting section 18.
  • a seal receiving portion 136 is disposed between the shoulder 132 and the securing portion 134.
  • an annular axial seal 138 is arranged, which rests on the sealing surface 130.
  • the axial seal 138 is pressed against the sealing surface 130 by a sealing surface 140 of a pumping cartridge 142.
  • the securing portion 134 causes the axial seal 138 can not fall radially inwardly and, secondly, that the axial seal 138 is not crushed. - -
  • the pumping cartridge 142 has a shape defined by the outer wall 13 of the pumping device 10 and an inlet-side bottom 144 and an outlet-side bottom 146 (FIG. 8).
  • the pumping cartridge 142 has a substantially cylindrical outer shape.
  • the pumping cartridge 142 Coaxially to the outer wall 13 of the pumping device 10, the pumping cartridge 142 has a central opening 148 on the main axis 11, through which the central armature 52, the electrical supply device 58 and the hollow shaft 92 extends.
  • the pump cartridge 142 has a housing 147 including an outer wall 143, the inlet side bottom 144, and the outlet side bottom 146.
  • the pump cartridge 142 is subdivided into, for example, four sections, which are arranged successively in the axial direction 19 (see FIG.
  • a first portion 150 is disposed adjacent to a first port side 151 of the pump cartridge 142 and is in the axial direction 19 through the inlet side bottom 144 and a first intermediate bottom 152, and radially outwardly through the outer wall 143 and radially inwardly through the central Opening 148 limited.
  • the inlet side bottom 144 has an annular flat wall 154 which extends radially inwardly from the outer wall 143 to a sealing portion 156.
  • the sealing surface 140 of the pump cartridge 142 is arranged at the drive section 12 facing side of the annular flat wall 154 adjacent to the outer wall 143.
  • the first connection side 151 includes the inlet side bottom 144, the sealing surface 140, an axial suction port 164, and the sealing portion 156.
  • the sealing portion 156 has a cylindrical shape. He has on the inside a sealing surface 158, on which a radial seal 160 is arranged. Between the radial seal 160 and an inner sleeve 162, the first axial suction opening 164 of the pumping cartridge 142 extends. - -
  • the first axial suction opening 164 forms an annular passage from the suction section 120 of the pumping device 10 into the pumping cartridge 142, in particular directly into the first section 150 of the pumping cartridge 142.
  • the inner sleeve 162 extends over the entire axial height of the pumping cartridge 142. To transmit a rotational movement, the inner sleeve 162 is held against rotation on the hollow shaft 92. In the axial direction 19, the inner sleeve 162 along the hollow shaft 92 is displaceable.
  • a mounting fuse 171 can be achieved, which ensures that the pump cartridge 142 is installed correctly.
  • the first portion 150 of the pumping cartridge 142 includes a first one
  • Pressure generating region 166 which is bounded by the inlet side bottom 144, by the inner sleeve 162, by the first intermediate bottom and by a first radial partition wall 168, which has a cylindrical shape.
  • the pumping cartridge 142 has at least one pumping element 169 for generating a pressure difference.
  • the pumping element 169 has a first impeller 170. This is arranged in the first pressure generating region 166 and held on the inner sleeve 162.
  • the first impeller 170 has a first wall 172 and a spaced second wall 174, with the first wall 172 and the second wall 174 having a substantially constant distance from each other ( Figures 8, 12).
  • the first wall 172 has an inner cylindrical portion 176, with which the first impeller 170 is held on the inner sleeve 162.
  • the cylindrical portion 176 extends from the axial suction port 164 in the axial direction 19 in the direction of the connection portion 18 to a curved transition portion 178, in which the first wall 172 of The first impeller 170 slopes outwardly and merges into a support portion 180.
  • the support portion 180 extends outwardly from the transition portion 178 to near the first radial partition wall 168.
  • the support portion 180 extends substantially perpendicular to the axial direction 19 or substantially conically outwardly.
  • the second wall 174 of the first impeller 170 has a cylindrical portion 182 which extends from the axial suction port 164 of the pump cartridge 142 in the axial direction 19 in the direction of the connecting portion 18 until it merges into a curved transition portion 184.
  • the cylindrical portion 182 abuts against the radial seal 160 so that there is a gap 186 between the cylindrical portion 182 of the second wall 174 and the cylindrical portion 176 of the first wall 172.
  • the first impeller 170 has a suction mouth 187, through which fluid 126 to be pumped is sucked to the first impeller 170 (FIG. 12).
  • the suction port 187 is disposed between the cylindrical portion 176 of the first wall 172 and the cylindrical portion 182 of the second wall 174.
  • the suction mouth 187 has a suction surface 189, through which the fluid 126 to be pumped is sucked into the first impeller 170.
  • the suction surface 189 is annular and extends between the cylindrical portion 176 of the first wall 172 and the cylindrical portion 182 of the second wall 174.
  • the curved transition section 184 of the second wall 174 merges into a support section 188 of the second wall 174.
  • the curved transition section 184 of the second wall 174 has a smaller radius than the curved transition section 178 of the first wall 172.
  • the distance between the first wall 172 and the second wall 174 is also in the region of the curved transition sections 184 and - -
  • 178 is approximately equal to the distance 186 between the first wall 172 and the second wall 174 in the region of the axial suction opening 164.
  • the support portion 188 of the second wall 174 extends radially outwardly from the curved transition portion 184 of the second wall 174 to near the first radial partition 168.
  • the support portion 188 extends substantially perpendicular to the axial direction 19 or Essentially cone-shaped to the outside.
  • the support portion 188 of the second wall 174 extends substantially parallel to the support portion 180 of the first wall 172. Between the first wall 172 and the second wall 174 of the first impeller 170 are disposed wing members 190 extending between the first wall 172 and the second wall 174 of the first impeller 170.
  • the wing elements 190 extend substantially perpendicular to the carrier section 180 and the carrier section 188. In particular, the wing elements 190 extend in a spiral radially outward direction.
  • the wing members 190 form channels 192 in the first impeller 170 between the first wall 172 and the second wall 174 extending from the suction mouth 187 to a radial exit opening 194.
  • the radial exit opening 194 is annular and is defined by the distance 188 between the support portion 188 of the second wall 174 and the support portion 180 of the first wall 172 in the vicinity of the first radial partition wall 168.
  • the first impeller 170 also rotates about the main axis 11 of the pumping device 10.
  • the winged elements 190 between the first wall 172 and the second wall 174 become the fluid to be pumped 126, which is located in the first pressure generating area 166, set in rotation. - -
  • the centrifugal force generated by the rotation pushes the fluid 126 to be pumped radially outward, thereby sucking it into the axial suction port 164 into the first impeller 170 and exiting through the radial discharge port 194 again.
  • the first radial partition wall 168 has one or more exit ports 196 through which fluid communication between the first pressure generating region 166 and at least one first fluid channel 198 is formed.
  • the outlet openings 196 extend only in sections in the circumferential direction.
  • the at least one fluid channel 198 connects the first pressure generating area 166 to a first return area 200 disposed in a third portion 202 of the pumping cartridge 142.
  • the first fluid channel 198 extends in the first section 150 of the pumping cartridge 142 between the first radial partition wall 168 and the outer wall 143 of the pumping cartridge 142 and in a second section 228 of the pumping cartridge 142 between a second radial partition wall 212 and the outer wall 143 of the pumping cartridge 142 in the axial direction 19, the at least one first fluid channel 198 extending in the circumferential direction only in sections, so that in the area between the first radial partition wall 168 and the outer wall 143 of the pumping cartridge 142 and the first radial partition wall 168 and the second radial partition wall 212 space is available in which, for example, further fluid channels can be arranged.
  • the at least one fluid channel 198 extends both in the axial direction 19 and in the circumferential direction, so that a helical formation from the first portion 150 to the third portion 202 is given.
  • the helical course is not necessarily completely circumferential; For example, it takes an angle of 90 °.
  • the first return region 200 extends in the radial direction from the outer wall 143 of the pumping cartridge 142 and the inner sleeve 162 of the pumping device 142. - - Cartridge 142 and in the axial direction 19 between a second intermediate bottom 206 and a third intermediate floor 208th
  • the second intermediate bottom 206 has an annular intermediate wall 210, which extends from the second radial partition 212 radially inwardly to a cylindrical wall-shaped sealing portion 214, which has a sealing surface 216 on its inner side. Adjacent to the sealing surface 216, a radial seal 218 is arranged.
  • annular axial suction port 220 is arranged between the inside of the radial seal 218 and the inner sleeve 162.
  • the axial suction port 220 provides fluid communication from the first return region 200 to a second pressure generating region 222.
  • the at least one fluid passage 198 and the first return area 200 form a fluid passage 204 between the exit port 196 of the first pressure generating area 166 and the axial suction port 220 of the second pressure generating area 222.
  • a second pumping element 223 is arranged, which comprises a second impeller 224, which is formed and arranged in mirror image to the first impeller 170.
  • the elements of the second impeller 224 are provided with the same reference numerals as the corresponding elements of the first impeller 170.
  • a mirror plane 226 is perpendicular to the main axis 11 and between the first pressure generating area 166 and the second pressure generating area 222.
  • the mirror-image arrangement of the second impeller 224 to the first impeller 170 within the pumping cartridge 142 causes the axial thrusts 225 acting on the impellers 170 and 224 to be pumped by pumping the fluid 126 to be pumped.
  • the axial thrust 225 acting on the impeller 170 results essentially from the generated pressure difference multiplied by the surface of the impeller. Suction surface 189 of the suction mouth 187. The same applies to the axial thrust, which acts on the second impeller 224.
  • the axial centering of the hollow shaft 92 can be achieved, for example, solely by the magnetic centering forces of the electric motor 72.
  • the second pressure generating area 222 is disposed in a second portion 228 of the pumping cartridge 142.
  • the second pressure generating region 222 extends in the axial direction 19 from the first intermediate bottom 152 to the second intermediate bottom 206 and in the radial direction from the inner sleeve 162 to the second radial dividing wall 212.
  • the second radial partition wall 212 has at least one outlet opening 230, which fluidly connects the pressure generating area 222 with at least one second fluid channel 232.
  • the at least one second fluid channel 232 is arranged offset in the circumferential direction to the at least one first fluid channel 198.
  • the at least one second fluid channel 232 connects the second section 228 of the pumping cartridge 142 to a fourth section 234 of the pumping cartridge 142.
  • the fourth section 234 is disposed adjacent to a second terminal side 241 of the pumping cartridge 142.
  • the fourth portion 234 includes a return and outlet portion 236 extending radially between the outer wall 143 of the pumping cartridge 142 and the inner sleeve 162 and extending in the axial direction 19 between the third intermediate bottom 208 and the outlet side bottom 146.
  • the outlet-side bottom 146 has an outer annular wall section 238, which merges at its inner side into a cylindrical wall-shaped securing section 240.
  • the outer annular wall portion 238 indicates - - Its the connection section 18 side facing an axial sealing surface 242, on which an axial seal 244 is arranged.
  • the securing portion 240 prevents the axial seal 244 from slipping radially inward from the axial sealing surface 242 and that the axial seal 244 is not crushed.
  • the securing portion 240 of the outlet-side bottom 146 is in an annular flat inner wall portion 246 via.
  • the inner wall portion 246 extends radially inward from the securing portion 240 to a radial distance from the main axis 11 of the pumping device 10 that corresponds to the radial distance of the outer surface of the sealing portion 156 of the inlet-side bottom 144 from the main axis 11 of the pumping device 10 so that a further identical pumping cartridge 142 can be placed on the pumping cartridge 142, and it can thereby fit flush in an outlet opening 248, which is arranged in the outlet side bottom 146.
  • the second port side 241 of the pump cartridge 142 includes the exhaust-side bottom 146, the securing portion 240, the axial sealing surface 242, the axial seal 244, and the annular inner wall portion 246.
  • the second connection side 241 and the first connection side 151 are formed complementary to each other.
  • Fluid (delivery fluid) 126 to be pumped is drawn into the first pressure generating region 166 through the axial suction port 164 during operation of the pumping cartridge 142, where it is rotated by the impeller 170, thereby exiting the impeller 170 through the radial discharge port 194. From there, the fluid 126 to be pumped flows through the at least one outlet opening 196 into the at least one first fluid channel 198.
  • the fluid 126 to be pumped is passed through the at least one first fluid channel 198 into the first return region 200, into which the fluid 126 to be pumped is recirculated radially inwards. - -
  • the fluid 126 to be pumped is sucked into the second suction port 220 and passed through it into the second pressure generating region 222.
  • the fluid 126 to be pumped enters the second impeller 224 and is rotated thereby, whereby it passes through a second radial outlet opening of the second impeller 224 through at least one outlet opening 230 of the second radial partition 212 into a fluid channel 232.
  • the fluid channel 232 directs the fluid 126 to be pumped into a return and outlet region 236 which is arranged in the fourth section 234 of the pumping cartridge 142.
  • the outlet opening 248 merges directly into an axial suction opening 164 on a further pumping cartridge 142 '. Due to the configuration of the pressure generating regions 166 and 222, the distance 186 between the first wall 172 and the second wall 174 of the impellers 170 and 224 can be varied. This makes it possible to use pumping cartridges with different pumping power, which have the same outer dimensions. Adjacent to the further pumping cartridge 142 ', the connecting portion 18 is arranged.
  • a special form of the pumping cartridge is an empty cartridge 249 (FIG. 13), which may be arranged as an alternative to the further pumping cartridge 142 'or to the first pumping cartridge 142.
  • the empty cartridge 249 has the same elements necessary for installation in the pumping device 10 as the pumping cartridge 142, 142 ', so that one of the pumping cartridges 142, 142' can be replaced by the empty cartridge 249. - -
  • the empty cartridge 249 has, in particular, the same diameter and the same height as the pumping cartridge 142, 142 'and a sealing surface 140, an inner sleeve 162, a further axial sealing surface 242 on which an axial seal 244 is secured, which is secured by a securing portion 240.
  • the empty cartridge 249 has a fluid passage 251 which extends in the axial direction over the entire length of the empty cartridge 249 from a suction port 164 to an outlet port 230 so that the fluid 126 to be pumped can flow unaffected by the empty cartridge 249.
  • the pumping capacity of the pumping device 10 can be adapted to the given requirements, for example by reducing the achievable pressure.
  • the connection section 18 has an end device 250 (see FIGS. 14, 15) which has an annular sealing surface 252 which faces the second pumping cartridge 142 'and on which the axial seal 244 rests in order to form a fluid-tight transition between the axial Sealing surface 242 of the pump cartridge 142; 142 'and the sealing surface 252 of the termination unit 250.
  • the annular sealing surface 252 includes a central opening 254 through which the fluid 126 to be delivered is pumped into the port portion 18. From there, the fluid 126 to be pumped is conducted via one or more fluid channels 256 to a central fluid outlet opening 258.
  • the central fluid outlet opening 258 is arranged coaxially with the main axis 11 of the pump device 10.
  • the central fluid outlet opening 258 is formed, for example, with an internal thread, so that a connection 259, for example a hose or pipe connection 259, can be fixed.
  • the fluid channels 256 lead the fluid to be pumped around a fixing and storage device 260 so that they are centrally located on the main shaft 11. may be ordered without impeding the flow of the fluid 126 to be pumped.
  • the fixing and bearing device 260 has an upper radial annular bearing 262, with which the hollow shaft 92 is mounted.
  • the upper radial ring bearing 262 has, for example, a plain bearing or a ball bearing.
  • the upper radial annular bearing 262 is arranged in a support section 264 of the fixing and bearing device 260 and supports the hollow shaft 92.
  • the support section 264 is held on an outer wall 268 of the connection section 18 via a plurality of reinforcing ribs 266.
  • the reinforcing ribs 266 extend in the radial and axial direction from the support portion 264 to the outer wall 268, so that a rotationally and translationally fixed connection between the support portion 264 and the outer wall 268 is formed.
  • the central armature 52 passes through the support section 264.
  • a securing section 265 of the central armature 52 passes through the support section 264.
  • the transition between the hollow shaft 92 and the support portion 264 is fluid-tightly sealed by a radial seal 263 disposed in the support portion 264 adjacent to the radial ring bearings 262.
  • a radial seal 270 is arranged, which fluid-tightly seals a transition between the central armature 52 and the support portion 264. Between the radial seal 270 and the radial seal 263, a region 271 is formed, which is not surrounded by fluid 126 to be pumped.
  • the central armature 52 extends from the base section 42 of the drive section 14 along the main axis 11 of the pump device 10 - - Through the remaining drive section 14 through the pump section 16 into the connection section 18th
  • the securing portion 265 of the central armature 52 has, for example, an (external) thread.
  • a retaining nut 272 is screwed onto this thread, so that the support section 264 is pressed in the axial direction (in the direction of the head section 12 of the pump device 10).
  • the central anchor 52 is held on the base portion 42 of the drive portion 14 by the holding device 50 and held at its other end by the retaining nut 272 on the support portion 264. In this way, the central armature 52 holds the driving portion 14, the pumping portion and the connecting portion 18 of the pumping device 10 together.
  • the hollow shaft 92 acts as a drive shaft 91 in the pumping device and transmits the drive power of the electric motor 72nd
  • the hollow shaft 92 extends from the motor base element 80, starting from the drive section 14 through the pump section 16 into the connection section 18.
  • the hollow shaft 92 is supported on its one side by the radial ring bearing 96 in the region of the motor 72 and on its other side the radial ring bearing 262 mounted on the support portion 64 coaxial with the main axis 11 of the pumping device 10 and coaxial with the central armature 52.
  • the inner diameter of the hollow shaft 92 is greater than the outer diameter of the central armature 52, so that a hollow cylindrical space 274 between the central armature 52 and the hollow shaft 92 is formed.
  • the electrical supply device 58 extends from the drive section 14, starting from the pump section 16 into the connection section 18. - -
  • the electrical supply device 58 extends from the connection section 18 into the drive section 14 within the free space 274.
  • the electrical conductors 56 of the electrical supply device 58 are formed flat and circular arc segment-like, so that they can be applied to the central armature 52.
  • an inner insulating layer 276 is disposed between the electrical conductors 56 and the armature 52, in particular the central armature 52, and a second outer insulating layer 278 is mounted on the outside of the electrical conductors 56. There is clearance between the outer insulating layer 278 and the inner wall of the hollow shaft 92 so that contact of the hollow shaft 92 with the outer insulating layer 278 during normal operation is excluded.
  • an electrical connection device 280 is arranged, which connects the electrical conductors 56 of the electrical supply device 58 with an electrical connection 282 of the pump device 10.
  • the electrical connection device 280 is arranged in the regions 271, which are not surrounded by the fluid 126 to be pumped, so that the electrical supply device 58 does not come into contact with the fluid 126 to be pumped.
  • Electrical isolation of the electrical connection device 280 is not necessary within the area 271 not surrounded by fluid 126 to be pumped.
  • the electrical connection device 280 has several, for example three, contact fingers 281, with which an electrical contact with the electrical conductors 56 of the electrical supply device 58 is produced (FIG. 16).
  • the contact fingers 281 have spring elements which are mechanically stressed when a unit from the central armature 52, the electrical conductors 56
  • the electrical supply device 58 and the hollow shaft 92 are arranged in the carrier section 264.
  • a drive unit 284 which has the drive section 14, the outer wall 13 of the pump device 10, the central armature 52 and the hollow shaft 92 with electrical supply device 58 extending therein, can be preassembled so that a receiving region 286 is formed, into which several, for example two , Pump cartridges 142, 142 'can be added.
  • the axial seal carrier 122 and the axial seal 138 form a cartridge port 287.
  • the cartridge port 287 is formed complementary to the first port side 151 of the pump cartridge 142.
  • Cartridge port 287 allows fluid communication of suction section 120 with suction port 164 of pumping cartridge 142.
  • the mounting of the two pump cartridges 142, 142 'in the receiving areas 286 can be done by simply inserting the pump cartridges 142.
  • the connecting portion 18 is placed on one end and fixed by means of the retaining nut 272, which is screwed onto the central anchor 52, in particular to the central anchor 52.
  • the connection section 18 is fixed to the drive unit 284.
  • a simple assembly of the pumping device 10 is made possible in that the hollow shaft 92 only in the region of the drive 62 by the radial ring bearing 96 and by the arranged in the connection section 18 radial ring - - Bearing 262 is stored. Thus, when inserting the pump cartridges 142, 142 'no additional bearings for the hollow shaft 92 must be installed.
  • a set of pumping cartridges 283 is provided that includes a plurality of pumping cartridges 142, 142 '.
  • the set of pumping cartridges 283 comprises a plurality of, for example, two pumping cartridges 142, 142 'of identical design and at least two differently designed pumping cartridges 142, 142'.
  • the pump cartridges 142, 142 ' can be designed differently, that the pumping power of the pump cartridges 142, 142' differs, for example, by the pressure difference obtained at a certain speed and resulting delivery head and / or in the achievable at a certain speed flow.
  • the pumping capacity of one pumping cartridge 142 may differ from the pumping capacity of another pumping cartridge 142 'in that the pumping cartridge 142 does not have any
  • a plurality of drive units 284 are provided which have different drive powers.
  • the drive power of the drive units 284 may differ in particular in the achievable speed and in the torque generated by the drive unit 284.
  • a wide range of requirements, such as head and flow rate can be covered.
  • a kit 285 may be provided that includes at least the set of pumping cartridges 283, a plurality of drive units 284 having different drive powers, the terminal portion 18, and a fastener 273, such as a retaining nut 272. - -
  • those pumping cartridges 142, 142 ' are selected from the set of pumping cartridges 283, which achieve the required flow rate. Furthermore, it can be determined, for example, whether a pumping cartridge 142, 142 'in conjunction with an empty cartridge 249 is sufficient without pumping power, or whether two or more pumping cartridges are required in order to achieve the required delivery heights.
  • the achievable delivery height depends on the one hand on the pump cartridge 142, 142 'and on the rotational speed of the drive unit 284, so that a corresponding drive unit 284 can be selected for a given delivery height and already selected pump cartridges 142, 142'.
  • the insertion takes place in that the pump cartridges 142, 142 'are each pushed with their inner sleeve 162 via the drive shaft 91.
  • the drive shaft 91 guides the pump cartridge 142 coaxially into the drive unit 284 until the sealing surface 140 of the pump cartridge 142 rests on the axial seal 138 of the drive unit 284.
  • the second pumping cartridge 142 ' is correspondingly inserted into the drive unit 284, so that the sealing surface 140 of the second pumping cartridge 142' rests on the axial seal 244 of the first pumping cartridge 142.
  • connection section 18 is placed on the drive unit 248.
  • the fitting of the connection section 18 onto the drive unit 284 takes place in that the central armature 52 is guided through the central opening 254 of the connection section 18 and through the support section 262 of the fixing and storage device 260 so that the hollow shaft 92 passes through the radial ring bearing 262 is stored and the securing portion 265 of the armature 52, in particular the central armature 52, beyond the support portion 264 addition.
  • the retaining nut 272 is screwed onto the securing section 265 of the armature, in particular of the central armature 52, thus pulling the armature 52 the drive section 14 to the terminal portion 18.
  • the second Pump cartridge 142 By this tensile force of the central armature 52 of the terminal portion 18 to the second Pump cartridge 142, the second pumping cartridge 142 to the first pumping cartridge 142 and the first pumping cartridge 142 on the cartridge port 287 pressed so that the respective axial seals are subjected to a force, so that these transitions are sealed.
  • the axial forces which occur due to the pumping which act, for example, on the housing 147 of the pumping cartridges 142, are thus transmitted into the connection section 18 by the armature 52, in particular by the central armature 52.
  • the outer wall 13 of the pumping device 10 thus does not have to withstand any axial tensile forces; in particular, no connections are required between the outer wall 13 of the pumping device and the connecting section 18, which can absorb the axial forces.
  • the outer wall 13 of the pumping device 10 can be made thinner than if the outer wall 13 of the pumping device 10 would have to absorb the axial forces.
  • near-axis portions of the pumping device 10 are utilized for power transmission in which the pressure generation by the vaned wheels 170 is less efficient.
  • the areas further out, in which pressure can be generated particularly efficiently, can be used for the generation of pressure.
  • the electrical supply device 58 extends within the hollow shaft 92, the electrical supply device 58 extends within an area close to the axis of the pump device 10 in which the generation of pressure is less effective.
  • the elimination of these areas, in which the electric supply direction 58 extends, is more favorable for the generation of pressure than if - - Off-axis areas for the electrical supply device 58 would have to be used, which then could not be used to generate pressure.
  • the impeller 170 and the impeller 224 are held on the same inner sleeve 262 in the axial direction 19. As a result, the axial forces acting on the impellers add up. Due to the mirror-image arrangement of the impeller 170 and the impeller 224 to each other, the axial forces acting on the impellers are just opposite, so that the addition of the axial forces just picks up.
  • the arrangement of the impellers 170 and 224 in the pump cartridge 142 and the arrangement of the fluid channels 198 and 232 can be achieved that in mirror image arrangement of the impellers 170 and 224 a pumping direction parallel to the drive axis 91 is achieved, the two impellers 170 and 224 fluidly effective are connected in series.
  • the assembly of the pumping device 10 is simplified since only the pumping cartridges 142 have to be inserted into the drive unit 284 without having to use radial bearings for the drive shaft 91 therebetween.
  • a second embodiment of a pumping device 10 shown in FIGS. 18 to 20 differs from the first embodiment of the pumping device 10 shown in FIGS. 1 to 17 in that the rotor 76 and the hollow shaft 92 have bores 290 which form a circulation - Allow a coolant 288 within the electric motor 72 and the hollow shaft 92.
  • the second embodiment of a pump device 10 differs from the first embodiment of the pump device 10 in that instead of a central armature 52, a tube 292 is guided in the hollow shaft 92 and that the hollow shaft 92 is mounted in the connection section 18 against the tube 292 and that Bearing is sealed against the fluid 126 to be pumped.
  • the coolant 288 includes, for example, a water-glycol mixture.
  • the bores 290 are arranged in the hollow shaft 92 in the region of the motor 72, and produce a fluid-effective connection between the interior of the hollow shaft 92 and an inner region of the electric motor 72nd
  • the rotor 76 bores 290, which are arranged in the connecting portion 104 of the rotor 76.
  • the holes 290 are arranged in the connecting portion 104 in alignment with the holes 290 in the hollow shaft 92.
  • the area 127 sealed with respect to the fluid 126 to be pumped is filled with the coolant 288.
  • the hollow shaft 92 and the rotor 76 rotate, thereby also causing coolant 288 to rotate.
  • the coolant 288 is pumped radially outward in the areas where the coolant 288 is in contact with rotating parts. For example, in an area between the annular base portion
  • the bores 290 now cause the coolant circuit 294 to extend between the stator 74 and the rotor 76 and thus cool the windings 70 of the stator 74, that is to say absorb the heat generated in the windings 70, and for the coolant circuit 294 extends between the rotor 76 and the outer wall 13 of the pumping device 10, at which the coolant 288 can deliver the heat absorbed via the outer wall 13 of the pumping device 10 to the environment.
  • the hollow shaft 92 has bores 290 which are arranged within the radial annular bearing 96, so that the coolant 288 can serve as a lubricant for the radial annular bearing 96.
  • the tube 292 within the support portion 264 viewed in the axial direction 19, from the motor 72, behind the radial ring bearing 262 borings 290 on which provide a fluid effective connection between the interior of the tube 292 and the exterior of the tube 292.
  • coolant 288 is sucked out of the region between the pipe 292 and the hollow shaft 92 and guided radially outwards in the region of the engine.
  • the coolant 288 is drawn through the bores 290 disposed in the tube 292 behind the second radial annular bearing 262 so that the coolant 288 can also serve as a lubricant for the second radial annular bearing 262 disposed in the support portion 264.
  • the coolant 288 is sucked into the tube 292 in the region of the motor 72, guided axially through the tube 292 in the direction of the connection section 18 and guided in the connection section 18 through the bore 290 radially outwards into the intermediate space between the hollow shaft 92 and the tube 292.
  • the second embodiment of the pump device 10 illustrated in FIGS. 18 to 20 is identical in construction and function to the first embodiment shown in FIGS. 1 to 17, to the above description of which reference is made in this respect.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Mining & Mineral Resources (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

L'invention concerne un dispositif de pompage (10) particulièrement compact, efficace et fiable, destiné à l'acheminement d'un fluide (126) à pomper, comprenant au moins une unité d'entraînement (284) possédant un dispositif d'entraînement (62) et au moins une partie de réception (286), sur laquelle au moins deux cartouches de pompe (142, 142') peuvent être montées hydrauliquement en série.
EP17731899.5A 2016-06-22 2017-06-21 Dispositif de pompage Withdrawn EP3475570A1 (fr)

Applications Claiming Priority (8)

Application Number Priority Date Filing Date Title
DE102016111427.8A DE102016111427A1 (de) 2016-06-22 2016-06-22 Pumpvorrichtung zur Förderung eines Fluids
DE102016111440.5A DE102016111440A1 (de) 2016-06-22 2016-06-22 Pumpvorrichtung zur Förderung eines Fluids
DE102016111408.1A DE102016111408A1 (de) 2016-06-22 2016-06-22 Pumpvorrichtung zur Förderung eines Fluids
DE102016111419.7A DE102016111419A1 (de) 2016-06-22 2016-06-22 Pumpvorrichtung zur Förderung eines zu pumpenden Fluids und Pumpkartusche
DE102016111406.5A DE102016111406A1 (de) 2016-06-22 2016-06-22 Bausatz für eine Pumpvorrichtung
DE102016111445.6A DE102016111445A1 (de) 2016-06-22 2016-06-22 Pumpvorrichtung zur Förderung eines Fluids
DE102016111414.6A DE102016111414A1 (de) 2016-06-22 2016-06-22 Pumpvorrichtung zur Förderung eines zu pumpenden Fluids
PCT/EP2017/065310 WO2017220693A1 (fr) 2016-06-22 2017-06-21 Dispositif de pompage

Publications (1)

Publication Number Publication Date
EP3475570A1 true EP3475570A1 (fr) 2019-05-01

Family

ID=59093576

Family Applications (1)

Application Number Title Priority Date Filing Date
EP17731899.5A Withdrawn EP3475570A1 (fr) 2016-06-22 2017-06-21 Dispositif de pompage

Country Status (4)

Country Link
US (1) US20190203723A1 (fr)
EP (1) EP3475570A1 (fr)
CN (1) CN109642558A (fr)
WO (1) WO2017220693A1 (fr)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110762026B (zh) * 2019-11-04 2021-06-15 中国船舶工业集团公司第七0八研究所 一种动力驱动轴系系统
DE102019133886B4 (de) * 2019-12-11 2024-12-05 Schaeffler Technologies AG & Co. KG Ableitvorrichtung mit Luftdurchlass sowie elektrische Antriebsanordnung mit der Ableitvorrichtung
WO2021261911A1 (fr) * 2020-06-23 2021-12-30 엘지이노텍 주식회사 Moteur
CN113404701B (zh) * 2021-06-17 2024-06-25 安徽新沪屏蔽泵有限责任公司 一种屏蔽泵
CN119957512B (zh) * 2024-12-20 2025-10-14 浙江大学高端装备研究院 一种冷却液循环泵

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1632357A (en) * 1926-05-24 1927-06-14 White Harry Pump or impeller
US1816731A (en) * 1930-02-10 1931-07-28 Jr John B Hawley Oil well pump
JPH1089260A (ja) * 1996-09-10 1998-04-07 Toshiba Corp 回転機械のクラック検出方法及びクラック検出装置
ES2628353T3 (es) * 2007-05-21 2017-08-02 Weir Minerals Australia Ltd Impulsor de bomba centrífuga con álabes auxiliares en la cubierta frontal, adyacentes a la abertura de entrada del impulsor
DE102012104311A1 (de) * 2012-05-18 2013-11-21 Xylem Ip Holdings Llc Anlaufmomentreduzierung für Pumpvorrichtungen

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US20190203723A1 (en) 2019-07-04
CN109642558A (zh) 2019-04-16
WO2017220693A1 (fr) 2017-12-28

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