EP4206470A1 - Roue de pompe, élément de carter et pompe l'utilisant - Google Patents

Roue de pompe, élément de carter et pompe l'utilisant Download PDF

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Publication number
EP4206470A1
EP4206470A1 EP23156384.2A EP23156384A EP4206470A1 EP 4206470 A1 EP4206470 A1 EP 4206470A1 EP 23156384 A EP23156384 A EP 23156384A EP 4206470 A1 EP4206470 A1 EP 4206470A1
Authority
EP
European Patent Office
Prior art keywords
pump
housing
blade
impeller
housing element
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.)
Pending
Application number
EP23156384.2A
Other languages
German (de)
English (en)
Inventor
Sascha Korupp
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.)
Herborner Pumpentechnik & Co KG GmbH
Original Assignee
Herborner Pumpentechnik & Co KG GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Herborner Pumpentechnik & Co KG GmbH filed Critical Herborner Pumpentechnik & Co KG GmbH
Publication of EP4206470A1 publication Critical patent/EP4206470A1/fr
Pending legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/18—Rotors
    • F04D29/22—Rotors specially for centrifugal pumps
    • F04D29/2238—Special flow patterns
    • F04D29/2244—Free vortex
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/18—Rotors
    • F04D29/22—Rotors specially for centrifugal pumps
    • F04D29/2261—Rotors specially for centrifugal pumps with special measures
    • F04D29/2288—Rotors specially for centrifugal pumps with special measures for comminuting, mixing or separating
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/18—Rotors
    • F04D29/22—Rotors specially for centrifugal pumps
    • F04D29/24—Vanes
    • F04D29/242—Geometry, shape
    • 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
    • F04D29/40—Casings; Connections of working fluid
    • 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
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/426—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for liquid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/426—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for liquid pumps
    • F04D29/4293—Details of fluid inlet or outlet
    • 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
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/44—Fluid-guiding means, e.g. diffusers
    • F04D29/441—Fluid-guiding means, e.g. diffusers especially adapted for elastic fluid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
    • F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps
    • F04D29/666—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps by means of rotor construction or layout, e.g. unequal distribution of blades or vanes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D7/00—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts
    • F04D7/02—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts of centrifugal type
    • F04D7/04—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts of centrifugal type the fluids being viscous or non-homogenous
    • 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
    • F05D2250/00—Geometry
    • F05D2250/60—Structure; Surface texture

Definitions

  • the invention relates to a housing element according to the preamble of claim 1.
  • the invention also relates to a pump, in particular according to claim 15, having such a housing element.
  • Vortex pumps are often used in waste water pumping. Wastewater is characterized by the fact that its exact composition is often unknown. The waste water often contains a high proportion of solids such as long-fibrous substances, coarse substances such as stones or chemically aggressive substances. Vortex pumps offer safe and robust pump operation, although their efficiency is often somewhat reduced compared to other pump hydraulics.
  • a pump impeller with two blade groups arranged opposite one another is known.
  • the blades have an inhomogeneous material thickness.
  • the object of the invention is to increase the efficiency of a pump and in particular a vortex impeller pump with the most constant possible power consumption and in this respect to optimize the flow control and thus the resource efficiency.
  • the solution should enable reliable, long-term operation and be cost-effective.
  • the housing element for a pump or a pump.
  • the housing element has an inner wall of the housing that delimits a flow channel for a fluid medium that extends along a central axis, the cross section of the flow channel becoming larger in a main flow direction.
  • the inner wall of the housing has a surface structure which is designed in such a way that it counteracts a backflow of the fluid medium counter to the main flow direction along the inner wall of the housing. This measure increases the pressure build-up in the pump housing because the backflow into the suction area of the pump is minimized.
  • the surface structure particularly favors the flow in the main flow direction. This accordingly minimizes a loss of performance of the pump and larger flow rates in particular are pumped more efficiently.
  • the flow control is optimized.
  • the surface structure can have at least one inflow surface which projects transversely into the return flow.
  • the inflow surface swirls the return flow and reduces it accordingly.
  • the surface structure has at least one step.
  • the shoulder forms the inflow surface and counteracts the backflow.
  • the shoulder forms a shadow for the main direction of flow, in which a negative pressure is created when the water flows over.
  • the return flow is then not only impeded at the shoulder, but the main flow then sucks the return flow back into the main flow.
  • the step can protrude transversely into the return flow.
  • the paragraph can be rotationally symmetrical.
  • the shoulder can be designed with an undercut, in particular in such a way that the backflow flows at least slightly under the shoulder. This undercut hardly disturbs the flow in the main flow direction. With regard to the return flow, the undercut can increase its deflection.
  • the undercut can form a radius for this. There should be no undercuts in the main flow direction. This improves demoldability. Draft angles of at least 1.5° are preferably maintained along the main flow direction. Besides that should not be formed in the main flow direction in the flow channel between several paragraphs tapers.
  • the at least one shoulder is designed in the shape of a ring or at least in the shape of a ring segment.
  • the annular or at least ring-segment-shaped step can run in a circumferential direction around the central axis.
  • the surface structure has at least one or two or three additional steps.
  • the shoulders are arranged at a distance from one another in relation to a direction radial to the central axis and/or the main direction of flow.
  • the distances and the number of paragraphs can be adjusted to the respective pump size.
  • the surface structure can also have at least five or at least six or at least ten or even significantly more than ten steps.
  • the surface structure resulting from the additional heels further reduces backflow.
  • the paragraph or paragraphs is a macrostructure.
  • the heel preferably has a heel height of at least 0.5 mm or at least 1.0 mm or at least 2.0 mm or at least 3.0 mm.
  • the further shoulders are preferably arranged at equal distances in the direction radially to the central axis and/or the main direction of flow.
  • the other paragraphs can be ring-shaped or at least ring-segment-shaped.
  • the further annular or at least annular shoulders can run in a circumferential direction around the central axis. This suppresses the backflow particularly efficiently.
  • the shoulder is designed spirally and is preferably wound radially outwards starting from the central axis, preferably by more than 360° or more than 720° or more than 1080° or even significantly more turns. This also allows the backflow to be efficiently suppressed.
  • the winding of the spiral shoulder which optionally increases in the direction of the pump impeller, improves the flow guidance in the direction of the pump impeller.
  • the shoulder has a wedge-shaped or trapezoidal cross-sectional profile.
  • This allows an undercut to be formed. It is about the basic form, whereby, for example, radii can also be formed on the edges. The return flow flows into this undercut and is slowed down. As a result, the backflow is suppressed particularly efficiently.
  • the fluid simply flows over the heel.
  • Further alternatives can have a round or oval cross-section.
  • numerous different basic shapes can be considered as the shape of the heel. However, these preferably do not form a flow obstacle in the main flow direction, but only against the main flow direction.
  • the step is stepped.
  • a step is characterized in particular by the fact that you walk down the step in the main flow direction and up the step in the opposite direction to the main flow direction. With optional multiple stepped landings, a staircase of steps results.
  • the inner wall of the housing has a conical basic shape on which the surface structure is formed.
  • the inner wall of the housing can preferably widen in the main direction of flow.
  • the housing element is thus particularly suitable for a vortex impeller pump.
  • the basic conical shape is preferably straight.
  • oblique conical basic shapes can also be considered, in particular slightly oblique conical basic shapes. This allows the pump connection to be positioned slightly differently, for example.
  • the conical basic shape is preferably a flat cone, namely in particular a cone with an opening angle of at least 20 degrees.
  • the housing element has a fluid inlet opening in the main flow direction at the start of the flow channel, with the fluid inlet opening being aligned with the central axis.
  • the fluid inlet opening can be arranged in the assembly, in particular in the area of the pump inlet.
  • a cover that forms the housing element can also be suitable for forming the pump inlet of a vortex impeller pump.
  • the housing element is designed as a detachable cover of a pump housing, in particular of the pump.
  • the cover is detachable in the sense that it is attached to at least one further element of the housing by means of at least one detachable fastening means.
  • Typical fasteners are screws and/or clamps.
  • the detachable cover can be designed with a fastening flange and preferably have screw holes. Since the cover is detachable, the housing element can be dismantled and then easily serviced and replaced where necessary. Alternatively or additionally, the housing element can form an impeller chamber of a pump housing.
  • a further alternative or supplementary configuration can consist in the housing element being an insert element in an impeller chamber of a pump housing.
  • Such insert elements can be installed inside an impeller chamber (eg screwed tight) and replaced if necessary, especially if, for example, abrasion or deposits impair the function of the shoulder or shoulders.
  • the invention is also achieved by a pump with a pump housing in which a pump impeller is rotatably mounted, with which a fluid medium can be conveyed from a pump inlet of the pump housing to a pump outlet of the pump housing, the pump housing having a housing element as described above and below , whose flow channel is arranged between the pump inlet and the pump impeller, and wherein the pump impeller is optionally designed as described below.
  • a pump with a pump housing in which a pump impeller is rotatably mounted, with which a fluid medium can be conveyed from a pump inlet of the pump housing to a pump outlet of the pump housing, the pump housing having a housing element as described above and below , whose flow channel is arranged between the pump inlet and the pump impeller, and wherein the pump impeller is optionally designed as described below.
  • the pump impeller is arranged opposite the housing element in the direction of the main flow direction.
  • the central axis of the housing member may be parallel and/or coaxial with the axis of rotation of the pump impeller.
  • the housing element advantageously forms a wall of a pump hydraulic system, with the pump impeller being arranged in an impeller chamber of the pump hydraulic system. It is preferably a radial pump hydraulic system.
  • the pump inlet should be flush with the pump impeller.
  • a free space without further flow guide elements is provided within the impeller chamber between the housing element and the pump impeller.
  • the pump outlet is preferably aligned orthogonally to the pump inlet and leads out radially from the pump impeller out of the impeller chamber.
  • a spiral fluid vortex forms between the pump inlet, which is formed by the housing element, and the pump impeller and leads to a backflow along the housing inner wall of the housing element, which then collides with the surface structure and swirls. The inhibition of the backflow is thus particularly effective.
  • the pump is a vortex pump.
  • the advantages mentioned are particularly important in the case of vortex impeller pumps.
  • the pump impeller has an impeller surface and a direction of rotation, blades being arranged on the impeller surface, with at least one of the blades is a first-type blade, and wherein the blade geometry of the first-type blade has a blade edge that is forwardly inclined in the direction of rotation.
  • the slope of this edge contributes to drawing the vortex that forms in front of the impeller into the impeller, in particular between the individual blades.
  • the incline can be formed by an incline and/or a radius.
  • the inclination can be designed to start at the impeller surface, or start at a distance from the impeller surface.
  • all of the blades of the pump impeller can be blades of the first type.
  • the efficiency of the pump impeller can be significantly increased compared to versions without such a blade edge.
  • the pump impeller has an impeller surface on which blades are arranged, with at least one of the blades being a blade of the first type, with at least one of the blades being a blade of the second type, with the blade geometry of the blade of the first type differing from the Blade geometry of the blade of the second type differs.
  • the blade geometry of the blade of the first type has a blade edge that is inclined forwards in the direction of rotation. These contribute in particular to conveying fluid into the space between the blades.
  • the pump impeller preferably has a (preferred) direction of rotation (hereinafter simply referred to as the direction of rotation, even if the impeller could theoretically also simply be driven to rotate backwards) and/or an imaginary axis of rotation about which the pump impeller should rotate during operation.
  • the imaginary axis of rotation (sometimes simply referred to below as the axis of rotation) runs, for example, through a wheel hub in the wheel surface, which is attached to a drive shaft is used.
  • the impeller hub can, for example, be a shaft mount and in particular designed as a bore in the impeller surface (eg with a keyway) or a shaft journal (eg with a keyway and/or eg cylindrical or conical).
  • the axis of rotation is aligned parallel and/or coaxially to the drive shaft and/or the bore. It runs transversely, preferably orthogonally, to the impeller surface.
  • the impeller surface should be formed by an impeller base or impeller plate, which is aligned transversely to the axis of rotation and through the center of which the axis of rotation runs.
  • the impeller surface is closed and designed in such a way that the pumped fluid leaves the impeller radially and is thus discharged transversely, in particular at right angles to the axis of rotation.
  • the blades have a blade pressure surface facing forward in the direction of rotation and a blade suction surface facing rearward in the direction of rotation.
  • the base body of the blade geometry of the blades of the first type and/or the blades of the second type can each extend outwards from the axis of rotation in such a way that it runs straight (straight blading) and is optionally aligned orthogonally to the axis of rotation.
  • the base body can have a curvature outwards from the axis of rotation (curved blading), which extends in particular over the impeller surface and is greater than 0° and up to 270°.
  • the impeller can be characterized in that the blade geometry of the blades of the first type and/or the blades of the second type has a convex blade pressure surface and/or a concave blade suction surface in a direction that runs radially outwards away from the axis of rotation.
  • the profile of the blade suction surface and/or the blade pressure surface can be in the form of a segment of a circle and/or a segment of a cylinder.
  • the pump impeller is suitable as a pump impeller for a vortex pump.
  • the blade pressure surface and/or the blade suction surface of the blade edge is inclined forwards in the direction of rotation.
  • the forward inclination has a positive effect on pressure build-up.
  • the blade of the first type can be divided along a curvature and/or along a kink into a base body and the blade edge, with the blade edge preferably being arranged at a distance from the impeller surface.
  • the inclination is realized by the curvature or the kink.
  • the blade edge can be inclined by an angle w1 with respect to an imaginary plane of rotation in which the impeller surface rotates (in operation) in the direction of rotation, the angle w1 preferably being between 55° and 87° or between 60° and 80° or between 65° and is 75°.
  • the blade geometry of the blade of the first type has a convex blade pressure surface and a concave blade suction surface, with the convex blade pressure surface having the angled blade edge and/or the concave blade suction surface having the angled blade edge.
  • the blade edge preferably has a free end which is not connected to any other element of the blade.
  • the blade edge is arranged on a base body of the blade geometry of the blade of the first type, the base body adjoining the impeller surface and in particular the blade edge being arranged at a distance from the base body and in particular forming a free end.
  • the basic body optimizes the impulse transmission to the fluid medium.
  • the blade geometry of the blade of the second type comprises a base body that adjoins the impeller surface and a blade cover that adjoins the base body, with a conveying channel being formed between the blade cover, the base body and the impeller surface.
  • the shovel cover contributes to optimized flow control as it reduces turbulence. In this respect, the turbulence in the conveying channel is reduced.
  • the conveying channel is delimited on three sides by the blade cover, the base body and the impeller surface. It ensures a higher dynamic pressure within the flow guided in it. In this case, it can be advantageous if the blade geometry of the blades of the first type does not have a blade cover.
  • the blades of the first type and second type are arranged alternately in the direction of rotation, the blades of the second type having blade covers and the blades of the first type having no blade covers.
  • the blades can be arranged with a uniform angular spacing.
  • the greater distance is then preferably formed between the optional blade edge and the opposite blade cover.
  • the greater blade spacing should be formed between the blade of the first type, which is equipped with a blade edge, and the second type of blade which is arranged in front of this in the direction of rotation and is equipped with a blade cover.
  • the opening angle between the blade pressure surface of the blade of the first type and the blade suction surface of a blade of the second type arranged in front of this in the direction of rotation is greater than the opening angle between the Blade pressure surface of the blade of the second type and the blade suction surface of a blade of the first type arranged in front of it in the direction of rotation.
  • the pump impeller has a direction of rotation and a blade channel formed between the blade of the second type and another of the blades in the direction of rotation is partially covered by the blade cover. This allows the flow guidance to be optimized particularly effectively and the turbulence to be minimized.
  • the partial cover ensures a sufficient inflow into the conveyor channel.
  • the blade cover can cover the blade channel by between 30% and 70% in the direction of rotation, so that a gap remains free along the blade channel.
  • the gap can extend over the full length of the blade channel, with the length extending radially to the axis of rotation, ie from the inside to the outside.
  • the blade cover covers a width of the blade channel, with the width extending in the direction of rotation.
  • the delivery channel is open at a radially outer blade wheel edge on the outer circumference of the pump impeller, so that a delivered fluid can exit the delivery channel radially to the axis of rotation. This aspect contributes to the fact that the flow guidance is further optimized and the turbulence is minimized.
  • the base body is aligned parallel to the axis of rotation with a maximum deviation of +/-20°, preferably +/-10°, more preferably +/-5° and particularly preferably +/-2°.
  • the base body can be aligned orthogonally to the impeller surface with a maximum deviation of +/- 20°, preferably +/- 10°, more preferably +/- 5° and particularly preferably +/- 2°. So the base body stands straight on the impeller surface or extends perpendicularly (+/- the specified deviation) away from the impeller surface.
  • the blade cover is aligned parallel to an imaginary plane of rotation with a maximum deviation of +/-20°, preferably +/-10°, more preferably +/-5° and particularly preferably +/-2° in which the impeller face rotates (in operation) in the direction of rotation, and/or is oriented orthogonally to the body.
  • the blade cover can be aligned parallel to the impeller surface with a maximum deviation of +/-20°, preferably +/-10°, more preferably +/-5° and particularly preferably +/-2°. This aspect also contributes to optimizing the flow control and minimizing turbulence.
  • the pump impeller has a direction of rotation and the blade cover protrudes beyond the base body in the opposite direction to the direction of rotation.
  • the conveying channel can be arranged behind the corresponding base body in the direction of rotation, with the surface of the base body adjoining the conveying channel preferably being the blade suction surface and the opposite side of the base body being a blade pressure surface. This measure also ensures an optimization of the flow control and a minimization of the turbulence.
  • the blade geometry of the blade of the first type and/or the blade of the second type has a homogeneous material thickness with a maximum deviation of +/- 30%, preferably +/- 20%, more preferably +/- 10% and more preferably +/- 5%.
  • the blade pressure surface and blade suction surface can run parallel.
  • the homogeneous material thickness optimizes the manufacturing process, especially the cooling process during casting.
  • the impeller is preferably made of metal. Due to the blade edge and blade cover described here, it is hardly possible to use a mold without cores anyway, which is why significantly less consideration needs to be given to draft angles and all surfaces can be optimized for efficiency.
  • the blades of the first type and the blades of the second type are arranged alternately one behind the other in a direction of rotation of the pump impeller.
  • the flow guidance through two adjacent blades influence each other directly.
  • the interaction of the different blade types is optimally utilized as a result.
  • the pump impeller is designed as a vortex impeller.
  • the impeller surface of the pump impeller is a closed surface and the axially flowing fluid is conveyed out of the region of the pump impeller radially to the axis of rotation. A deflection of the flow guidance is thus achieved.
  • a pump impeller 1 has an imaginary axis of rotation DA, about which the pump impeller 1 is intended to rotate during operation (hereinafter simply referred to as axis of rotation DA).
  • the axis of rotation DA runs through a wheel hub 14 in the middle of a wheel surface 11 , the wheel hub 14 having a keyway 15 .
  • a shaft of a drive unit of a pump can be accommodated with the impeller hub 14 .
  • the axis of rotation DA is coaxial with the impeller hub 14.
  • the impeller surface 11 is closed and designed in such a way that a pumped fluid leaves the pump impeller 1 radially. The pumped fluid is discharged at right angles to the axis of rotation DA.
  • the pump impeller 1 also has three blades of the first type 2 and three blades of the second type 3 which are arranged on the impeller face 11 .
  • the impeller surface 11 is aligned orthogonally to the axis of rotation DA and the pump impeller 1 is designed as a vortex impeller.
  • the impeller surface 11 is designed to be closed between the blades 2, 3, so that no fluid can pass through the pump impeller 1 parallel to the axis of rotation DA.
  • the pump impeller 1 can be rotated about the axis of rotation DA in a direction of rotation DR. This is the direction of rotation DR that is preferred during operation.
  • the blades of the first type 2 and the blades of the second type 3 are arranged alternately one behind the other in the direction of rotation DR.
  • the blades of the first type 2 have a blade pressure surface 24 and a blade suction surface 23 .
  • the blades of the second type 3 correspondingly have a blade pressure surface 34 and a blade suction surface 35 .
  • the blade pressure surfaces 24 each extend convexly in a direction R radially away from the axis of rotation DA.
  • the blade suction surfaces 23 are each concave in the direction R, which corresponds to the radius. This results in a so-called curved blading.
  • the blade pressure surfaces 24 and blade suction surfaces 23 form segments of a circle.
  • the blades of the first type 2 and second type 3 have a homogeneous material thickness 25, 37. That's the progression of the respective blade pressure surface 24, 34 and blade suction surface 23, 35 at least essentially parallel.
  • the blade geometry of the blade of the first type 2 differs from the blade geometry of the blade of the second type 3.
  • the blade geometry of the blade of the first type 2 has a base body 21 which adjoins the impeller surface 11 .
  • the base body 21 runs parallel to the axis of rotation DA and is aligned orthogonally to the impeller surface 11 .
  • a blade edge 22 adjoins the base body 21 .
  • the blade edge 22 is spaced apart from the impeller surface 11.
  • a curvature 27 runs between the base body 21 and the blade edge 22. Alternatively, it can be a kink. Due to the curvature 27, the blade edge 22 is inclined by an angle w1 of approximately 70° with respect to an imaginary plane of rotation in which the impeller face 11 rotates (in operation) in the direction of rotation DR.
  • the angle w1 should be between 55° and 87°, or between 60° and 80°, or between 65° and 75°.
  • blade edge 22 is inclined at an angle w2 of approximately 20° relative to base body 11, which is oriented orthogonally to the plane of rotation. Due to the homogeneous material thicknesses 25, 37 blade pressure surface 24 and blade suction surface 23 are parallel. Thus, both blade pressure surface 24 and blade suction surface 23 are inclined at angles w1 and w2.
  • the blade edge 22 and with it both the blade pressure surface 24 and the blade suction surface 25 are inclined forwards in the direction of rotation DR.
  • the blade edge 22 has a free end 26 in that no further element is connected to the blade edge 22 .
  • the base body 21 together with the blade edge 22 forms the blade pressure surface 24 and the blade suction surface 23 .
  • the blade of the second type 3 has a base body 31 and a blade cover 32 .
  • the base body 31 adjoins the impeller surface 11 and is aligned orthogonally with respect to the base body 31 .
  • the base body 31 is aligned parallel to the axis of rotation DA.
  • the blade cover 32 adjoins the base body 31 and is arranged at a distance from the impeller surface 11 .
  • the blade cover 32 is oriented parallel to the imaginary plane of rotation in which the impeller face 11 rotates (in operation) in the direction of rotation DR.
  • a delivery channel 13 designed in this way is delimited on three sides by the blade cover 32, the base body 31 and the impeller surface 11.
  • the blade cover 32 is also aligned orthogonally to the base body 31 and the axis of rotation DA.
  • the blade cover 32 is also aligned parallel to the impeller surface 11 .
  • the blade cover 32 protrudes over the base body 31 counter to the direction of rotation DR, and therefore over the blade suction surface 35.
  • the delivery channel 13 is delimited between the blade suction surface 35 of the base body 31 and the blade cover 32 of the blade of the second type 3 and the impeller surface 11 .
  • a blade channel 12 is formed between blades 2, 3 that are adjacent in the direction of rotation DR.
  • a part of the blade channel 12 is formed by the conveying channel 13 .
  • the blade channel 12 is partially covered by the blade cover 32 by about 25-75%, so that a gap 16 remains free along the blade channel 12 for the inflow of fluid.
  • the gap 16 extends over the full length I of the impeller channel 12, the length I running radially to the axis of rotation DA.
  • the blade cover 22 covers the width b of the blade channel 12, the width b extending in the direction of rotation DR.
  • the delivery channel 13 is open at a radially outer blade wheel edge 17 so that a delivered fluid can exit the delivery channel 13 in the radial direction R.
  • the impeller edge 17 is on the outer circumference of the pump impeller 1.
  • a in 3 shown pump impeller 1 differs from the pump impeller Figures 1 and 2 that this has 3 blades of the first type 2 instead of the three blades of the second type.
  • the pump impeller 1 therefore only has blades of the first type 2, specifically six in this case.
  • the schematic sketch of 4 shows a development of a pump impeller 1, wherein the blade geometries are so different from those of 3 distinguish that the blade edge 22 does not form a free end 26. Instead, this is followed by a blade cover 32, which basically has the same features as the blade cover of the blades of the second type 3 in FIG Figures 1 and 2 . While the blade edge 22 is inclined forwards in the direction of rotation, ie in the direction of the blade pressure surface 24 , the blade cover 32 protrudes backwards from the end of the blade edge 22 in the direction of rotation, in particular beyond the blade suction surface 23 .
  • a further modification of the pump impeller 1 according to the invention can consist in the fact that, in contrast to the representation of the Figures 1 and 2 it is provided that pairs of a blade of the first type 2 and a blade of the second type 3 can be provided, with a larger blade spacing being formed between the first type of blade 2 equipped with blade edge 22 and the adjacent second type of blade 3 equipped with blade cover 32.
  • the included angle between the blade pressure surface 24 of the blade of the first type 2 and the blade suction surface 35 of an adjacently arranged blade of the second type 3 should be greater than the included angle between the blade pressure surface 34 of the blade of the second type 3 and the blade suction surface 23 of an adjacently arranged blade of the first type 2.
  • a housing element 100 is designed as a detachable cover, in particular with a fastening flange, of a pump 200.
  • the housing member 100 advantageously has screw holes 107 in the mounting flange.
  • the housing element 100 also has a housing inner wall 103 .
  • the housing inner wall 103 has a conical basic shape that extends along a central axis M.
  • the housing inner wall 103 delimits a flow channel 105 for a fluid medium that can be conveyed in a main flow direction H through the flow channel 105 .
  • the main flow direction H is coaxial to the central axis M.
  • a fluid inlet opening 104 is provided at the beginning.
  • the flow channel 105 widens in the main flow direction H.
  • the surface structure 101 is designed in such a way that it counteracts a return flow against the main flow direction H along the inner wall 103 of the housing.
  • the surface structure 101 has an inflow surface 106 which projects transversely into the return flow.
  • the inflow surface 106 has a plurality of shoulders 102 which form an undercut in relation to the conical inner wall 103 of the housing.
  • the paragraphs 102 are each formed rotationally symmetrically with respect to the central axis M.
  • the shoulder 102 is ring-shaped, with the shoulder running in a circumferential direction U around the central axis M.
  • a total of four paragraphs 102 are provided in the present case, it also being possible for more or fewer paragraphs 102 to be provided.
  • the shoulders 102 are arranged at equal intervals in the main flow direction H and in a direction R2 radial thereto.
  • the paragraphs 102 each run parallel to one another.
  • the other paragraphs 102, the number of which is variable, are also annular.
  • the paragraphs 102 according to 7 be designed in the form of a ring segment, with the shoulders 102 running in the circumferential direction U around the central axis M and being arranged at equal distances in the main flow direction H and the direction R2.
  • Another possibility is to form the shoulder 102 in a spiral shape, which is wound radially outwards towards the central axis M, as shown in FIG 8 shows.
  • a shoulder 102 has a wedge-shaped cross-section Q.
  • the paragraph 102 can also have a trapezoidal cross-section Q according to the 10 exhibit.
  • Further alternatives can have a round or oval cross-section.
  • a gradual cross-sectional narrowing results in the direction opposite to the main flow direction H.
  • a pump 200 according to the invention which is designed as a free-flow impeller pump, demonstrates 11 a pump housing 201 on.
  • a pump impeller 1 according to the invention is provided, as is the case, for example, in FIGS Figures 1, 2 , 3 and 4 is shown.
  • the pump impeller 1 is rotatably mounted and is driven by a drive unit 202 .
  • the fluid medium can be conveyed through the pump housing 201 from a pump inlet 203 to a pump outlet 204 .
  • the pump inlet 203 and the pump outlet 204 are aligned orthogonally to one another.
  • the pump outlet 204 leads out radially from the pump impeller 1 out of an impeller chamber 206 in which the pump impeller 1 is located.
  • the pump housing 201 has a housing element 100 according to the invention.
  • the housing element 100 forms a wall of the impeller chamber 206 .
  • the pump impeller 1 is arranged opposite the housing element 100 in the main flow direction H, with the central axis M being parallel and coaxial with the axis of rotation DA.
  • the fluid inlet opening 104 of the housing element 100 is in the region of the pump inlet 203.
  • the flow channel 105 is arranged between the pump inlet 203 and the pump impeller 1. In the flow channel 105 and between the pump inlet 203 and the pump impeller 1, a free space 207 is formed, in which no further flow guide elements are provided. A vortex forms in this space 207 because the fluid is excited by the pump impeller 1 to rotate.
  • An overpressure at the pump outlet 204 then leads to a backflow on the inner wall of the housing element 100.
  • the shoulders here form flow obstacles for the backflow and direct the backflow back into the main flow direction H.
  • the housing element 100 can be designed as a detachable cover with a fastening flange and can be fastened to the rest of the pump housing 201 by means of screws as fastening means.
  • a further alternative can be that the housing element 100 is inserted into the interior of the pump housing 101 as an insert.
  • the pump housing 101 should form a seat for the housing element.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Geometry (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
EP23156384.2A 2021-04-28 2022-04-25 Roue de pompe, élément de carter et pompe l'utilisant Pending EP4206470A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102021110936.1A DE102021110936A1 (de) 2021-04-28 2021-04-28 Pumpenlaufrad, Gehäuseelement und Pumpe hiermit
EP22169868.1A EP4083430A1 (fr) 2021-04-28 2022-04-25 Rotor de pompe, élément de logement et pompe associée

Related Parent Applications (1)

Application Number Title Priority Date Filing Date
EP22169868.1A Division EP4083430A1 (fr) 2021-04-28 2022-04-25 Rotor de pompe, élément de logement et pompe associée

Publications (1)

Publication Number Publication Date
EP4206470A1 true EP4206470A1 (fr) 2023-07-05

Family

ID=81387184

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Application Number Title Priority Date Filing Date
EP22169868.1A Pending EP4083430A1 (fr) 2021-04-28 2022-04-25 Rotor de pompe, élément de logement et pompe associée
EP23156384.2A Pending EP4206470A1 (fr) 2021-04-28 2022-04-25 Roue de pompe, élément de carter et pompe l'utilisant

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EP22169868.1A Pending EP4083430A1 (fr) 2021-04-28 2022-04-25 Rotor de pompe, élément de logement et pompe associée

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US (2) US11761453B2 (fr)
EP (2) EP4083430A1 (fr)
DE (1) DE102021110936A1 (fr)

Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4475868A (en) * 1981-12-08 1984-10-09 Emile Egger & Cie Sa Free-flow-pump
DE3520263A1 (de) 1984-08-16 1986-12-04 Osakeyhtiö E. Sarlin AB, Helsinki Laufrad fuer eine pumpe, besonders fuer eine wirbelstrompumpe
JPH094585A (ja) * 1995-06-20 1997-01-07 Torishima Pump Mfg Co Ltd 汚水ポンプ
EP1134420A2 (fr) * 2000-03-15 2001-09-19 FHP Motors GmbH Pompe centrifuge avec structure de surface améliorant l'écoulement
US20050207891A1 (en) * 2003-07-01 2005-09-22 Shaw James G Impeller vane configuration for a centrifugal pump
EP1616100A1 (fr) * 2003-01-17 2006-01-18 KSB Aktiengesellschaft Pompe non colmatable
US20070274820A1 (en) * 2003-10-20 2007-11-29 Martin Lindskog Centrifugal Pump
US20140030086A1 (en) * 2012-07-26 2014-01-30 GM Global Technology Operations LLC Centrifugal pump
WO2016165795A1 (fr) * 2015-04-15 2016-10-20 Sulzer Management Ag Turbine pour une pompe centrifuge d'alimentation de caisse d'arrivée
WO2017001340A1 (fr) 2015-06-30 2017-01-05 Ksb Aktiengesellschaft Pompe non colmatable
US20200040915A1 (en) * 2018-08-01 2020-02-06 Liberty Pumps, Inc. Self-cleaning pump
US20210003134A1 (en) * 2019-07-02 2021-01-07 Dab Pumps S.P.A. Impeller for centrifugal pump, particularly for pump of the recessed impeller type, and pump with such an impeller

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3704360A1 (de) 1987-02-12 1988-08-25 Klein Schanzlin & Becker Ag Kreiselpumpe zur foerderung von feststoffhaltigen fluessigkeiten
EP2150705A4 (fr) * 2007-06-01 2014-07-30 Gorman Rupp Co Pompe, et turbine de pompe
DE102015211173A1 (de) 2015-06-17 2016-07-14 Mtu Friedrichshafen Gmbh Schaufelanordnung, Radialmaschine und Abgasturbolader
EP3835591B1 (fr) * 2019-12-13 2023-08-02 Dab Pumps S.p.A. Turbine pour pompe centrifuge, en particulier pour une pompe à turbine encastrée et pompe comportant une telle turbine

Patent Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4475868A (en) * 1981-12-08 1984-10-09 Emile Egger & Cie Sa Free-flow-pump
DE3520263A1 (de) 1984-08-16 1986-12-04 Osakeyhtiö E. Sarlin AB, Helsinki Laufrad fuer eine pumpe, besonders fuer eine wirbelstrompumpe
JPH094585A (ja) * 1995-06-20 1997-01-07 Torishima Pump Mfg Co Ltd 汚水ポンプ
EP1134420A2 (fr) * 2000-03-15 2001-09-19 FHP Motors GmbH Pompe centrifuge avec structure de surface améliorant l'écoulement
EP1616100A1 (fr) * 2003-01-17 2006-01-18 KSB Aktiengesellschaft Pompe non colmatable
US20050207891A1 (en) * 2003-07-01 2005-09-22 Shaw James G Impeller vane configuration for a centrifugal pump
US20070274820A1 (en) * 2003-10-20 2007-11-29 Martin Lindskog Centrifugal Pump
US20140030086A1 (en) * 2012-07-26 2014-01-30 GM Global Technology Operations LLC Centrifugal pump
WO2016165795A1 (fr) * 2015-04-15 2016-10-20 Sulzer Management Ag Turbine pour une pompe centrifuge d'alimentation de caisse d'arrivée
WO2017001340A1 (fr) 2015-06-30 2017-01-05 Ksb Aktiengesellschaft Pompe non colmatable
US20200040915A1 (en) * 2018-08-01 2020-02-06 Liberty Pumps, Inc. Self-cleaning pump
US20210003134A1 (en) * 2019-07-02 2021-01-07 Dab Pumps S.P.A. Impeller for centrifugal pump, particularly for pump of the recessed impeller type, and pump with such an impeller

Also Published As

Publication number Publication date
US20230175519A1 (en) 2023-06-08
DE102021110936A1 (de) 2022-11-03
US11761453B2 (en) 2023-09-19
EP4083430A1 (fr) 2022-11-02
US20220349418A1 (en) 2022-11-03

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