EP4130485A1 - Roue de pompe à fluide et pompe comprenant ladite roue - Google Patents

Roue de pompe à fluide et pompe comprenant ladite roue Download PDF

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Publication number
EP4130485A1
EP4130485A1 EP21189275.7A EP21189275A EP4130485A1 EP 4130485 A1 EP4130485 A1 EP 4130485A1 EP 21189275 A EP21189275 A EP 21189275A EP 4130485 A1 EP4130485 A1 EP 4130485A1
Authority
EP
European Patent Office
Prior art keywords
impeller
pump plate
side edge
fluid
blade
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Withdrawn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
EP21189275.7A
Other languages
German (de)
English (en)
Inventor
Frederic HACKL
Hubert UNTERBERGER
Mladen GOJKIC
Michael Ullrich
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.)
Bleckmann GmbH and Co KG
Original Assignee
Bleckmann GmbH and Co KG
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 Bleckmann GmbH and Co KG filed Critical Bleckmann GmbH and Co KG
Priority to EP21189275.7A priority Critical patent/EP4130485A1/fr
Priority to PCT/EP2022/071822 priority patent/WO2023012219A1/fr
Publication of EP4130485A1 publication Critical patent/EP4130485A1/fr
Withdrawn legal-status Critical Current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
    • F04D29/2205—Conventional flow pattern
    • F04D29/2216—Shape, geometry
    • 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
    • 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
    • F05D2240/20—Rotors
    • F05D2240/30—Characteristics of rotor blades, i.e. of any element transforming dynamic fluid energy to or from rotational energy and being attached to a rotor
    • F05D2240/304—Characteristics of rotor blades, i.e. of any element transforming dynamic fluid energy to or from rotational energy and being attached to a rotor related to the trailing edge of a rotor blade
    • 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
    • F05D2240/20—Rotors
    • F05D2240/30—Characteristics of rotor blades, i.e. of any element transforming dynamic fluid energy to or from rotational energy and being attached to a rotor
    • F05D2240/306—Characteristics of rotor blades, i.e. of any element transforming dynamic fluid energy to or from rotational energy and being attached to a rotor related to the suction side of a rotor blade
    • 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
    • F05D2250/70—Shape
    • F05D2250/71—Shape curved
    • F05D2250/711—Shape curved convex

Definitions

  • the present invention relates to an impeller for a fluid pump, in particular for a centrifugal pump for fluid, and a pump, in particular for domestic appliances such as dishwashers, including inter alia the impeller.
  • pumps including at least one impeller, are used to circulate fluid in a pumping chamber.
  • the impeller includes a top plate having a central opening and an opposing bottom plate, wherein vertical aligned blades are arranged therebetween.
  • a rotor shaft is coupled to a central recess of the bottom plate to rotate the impeller about its rotational axis.
  • the blades are curved in a direction perpendicular to the rotational axis of the impeller to form a C-shape, seen from a top sectional view, wherein the blades extend from the center to an outer circumference of the top plate and the bottom plate, respectively.
  • fluid enters the impeller at the central opening, flows through an interior formed by the top plate and the bottom plate, and out in the direction perpendicular to the rotational axis of the impeller at the outer circumference of the top plate and the bottom plate.
  • Such a pump including an impeller is disclosed in DE 10 2006 023 856 A1 .
  • the impeller includes six blades extending from the rotational axis of the impeller in the direction perpendicular to the rotational axis to an outer circumference of the impeller. Further, the blades are curved in a direction perpendicular to the rotational axis of the impeller forming a C-shape.
  • the following description contains specific information pertaining to implementations in the present disclosure.
  • the present application discloses an impeller for a fluid pump, in particular for a centrifugal pump for fluid, and a pump, in particular for domestic appliances such as dishwashers, including the impeller.
  • an impeller for a centrifugal pump for fluid comprises a lower pump plate having at least one coupling section configured to be coupled to a rotor shaft for driving the impeller about its rotational axis, an upper pump plate opposing the lower pump plate and having a central opening for providing an inlet for a fluid to be pumped, and a plurality of blades arranged between the lower pump plate and the upper pump plate, wherein the upper pump plate and the lower pump plate both have an outer circumference forming an outlet for the pumped fluid, wherein the fluid flows in a fluid flow direction from the fluid inlet through a pump interior formed by the lower and the upper pump plate, and out at the fluid outlet, wherein each of the blades has a suction surface, a pressure surface opposing the suction surface, side edges and a longitudinal axis extending at least substantially in fluid flow direction: a first longitudinal side edge of each blade being attached to the upper pump plate, a second longitudinal side edge of each blade opposing the first longitudinal side edge, and being attached to
  • each blade Due to the convex curvature of the suction surface of each blade, the fluid dynamics of the fluid flow flowing through the impeller can be enhanced. Thus, efficiency of the impeller improves, consequently. Further, the outflow side edge of each blade may be arranged substantially perpendicular to the lower pump plate and the upper pump plate.
  • an impeller for a fluid pump comprises a lower pump plate having at least one coupling section configured to be coupled to a rotor shaft for driving the impeller about its rotational axis, an upper pump plate opposing the lower pump plate and having a central opening for providing an inlet for a fluid to be pumped, and a plurality of blades arranged between the lower pump plate and the upper pump plate, wherein the upper pump plate and the lower pump plate both have an outer circumference forming an outlet for the pumped fluid, wherein the fluid flows in a fluid flow direction from the fluid inlet through a pump interior formed by the lower and the upper pump plate, and out at the fluid outlet, wherein each of the blades has a suction surface, a pressure surface opposing the suction surface, side edges and a longitudinal axis extending at least substantially in fluid flow direction: a first longitudinal side edge of each blade being attached to the upper pump plate, a second longitudinal side edge of each blade opposing the first longitudinal side edge, and being attached to the lower pump plate,
  • the acute angle between the outflow side edge and the lower pump plate may face towards the rotational direction of the impeller.
  • An acute angle is an angle that measures between 90° and 0°, meaning it is smaller than a right angle (an "L" shape) but has at least some space between the two lines that form it. Due to the inclination or rather oblique alignment of each of the blades, the fluid dynamics of the fluid flow flowing through the impeller can be enhanced. Thus, efficiency of the impeller improves, consequently.
  • each blade may have at least partially a convex curvature extending at least substantially in the direction of the rotational axis of the impeller. As a result, efficiency of the impeller may be enhanced even further.
  • the pressure surface of each blade has at least partially a concave curvature extending at least substantially in the direction of the rotational axis of the impeller. According to this, the fluid dynamics of the fluid flow flowing through the impeller may be enhanced. In particular, this can reduce turbulence in the impeller. According to a further embodiment, the suction surface of each blade has at least partially a concave shape, wherein the pressure surface of each blade has at least partially a convex shape.
  • the convex and/or concave curvatures extend substantially along the entire surface of each blade in direction of the longitudinal axis extending at least substantially in fluid flow direction.
  • the inflow side edge and/or the outflow side edge of each blade is curved substantially in the direction of the rotational axis of the impeller.
  • each blade is torqued in the direction perpendicular to the rotational axis of the impeller. Further, instead of the convex and/or concave curvatures of each blade, each blade may only be torqued. Independently of the angle formed between the outflow side edge of each blade and the lower pump plate of the impeller. Each blade may further have the shape of a helix extending substantially along the longitudinal axis of the respective blade.
  • an upper section of each blade formed between the first longitudinal side edge and the inflow side edge, extends at least partially into the central opening of the upper pump plate, preferably having a substantially frustum shape with a rounded outer circumference.
  • the height of each blade measured from the first longitudinal side edge to the second longitudinal side edge decreases in the direction perpendicular to the rotational axis of the impeller, preferably decreases steadily.
  • the slope of the first longitudinal side edge and/or the second longitudinal side edge may change at any point, even a turning point in the path of the first longitudinal side edge and/or the second longitudinal side edge is possible.
  • each blade may terminate at the outer circumference of the lower pump plate and the upper pump plate. According to a further feature, each blade may terminate at a predefined distance just before the outer circumference of the lower pump plate and the upper pump plate, i.e. the fluid outlet.
  • the outer circumference of the lower pump plate is larger than the outer circumference of the upper pump plate. This increases the outlet surface of the fluid outlet.
  • the inflow side edge is arranged in an acute angle to the lower pump plate, wherein the inflow side edge and the outflow side edge preferably have the identical acute angle with respect to the lower pump plate.
  • the lower pump plate comprises a cross-section which corresponds to a hat-like trapezoid with rounded edges, and wherein the hat-like trapezoid with rounded edges preferably corresponds to a bell-like trapezoid with rounded edges.
  • the upper pump plate comprises a cross-section which decreases from the inside to the outside, preferably decreases steadily.
  • each blade comprises a cross-section which has a wave-form, and wherein the wave-form includes at least one upward portion and one downward portion.
  • a pump in particular for domestic appliances such as dishwashers, comprises: a pumping chamber including a central axial fluid inlet and a tangential fluid outlet, an impeller according to any of claims 1 to 14 for conveying fluid, wherein the impeller rotating within the pumping chamber, and a motor including a rotor shaft, wherein the rotor shaft is attached to the at least one coupling section of the impeller.
  • the pump may be a centrifugal pump for fluid.
  • the pump may further include a heating unit for heating up the fluid flowing through the pump.
  • each blade of the impeller may be circularly arranged in regular intervals from each other between the lower pump plate and the upper pump plate.
  • three to nine blades are arranged between the lower pump plate and the upper pump plate, further preferably four to seven blades, and further more preferably five to six blades.
  • the impeller may further comprise a plurality of sub-blades arranged between the lower pump plate and the upper pump plate, and extending from the outer circumference of the lower pump plate and the upper pump plate to the interior formed by the lower pump plate and the upper pump plate, wherein the radial extension of the sub-blades is less than the radial extension of the blades.
  • Sub-blades increase the pressure inside the impeller and thereby enhancing efficiency of a pump including the impeller.
  • Each sub-blade opposing two blades and is associated to a respective blade, wherein a distance between a sub-blade to an associated blade may be different to another opposing blade.
  • Each sub-blade may be torqued in the direction perpendicular to the rotational axis of the impeller.
  • each blade and/or each sub-blade of the impeller may be tapered towards the respective inflow side edge. This, enhances fluid flow through the impeller.
  • each blade may have a fin-like shape, wherein an innermost portion of the blade, which is the first to be flowed by the fluid, corresponds to the shape of a front fin of a dolphin and the outermost portion of the blade corresponds to the shape of a back fin of a dolphin.
  • the impeller is made of a metal.
  • the impeller is made of a corrosion-resistant metal, such as stainless steel or high-alloy steel.
  • a corrosion-resistant metal such as stainless steel or high-alloy steel.
  • it can be used in a washing machine or dishwasher, for example it is resistant not only to the water being pumped, but also to the chemically but also against the chemically and mechanically aggressive substances ingredients, especially in a dishwasher.
  • the impeller may further comprise an upper ring plate, which is formed near the outer circumference of the upper pump plate and is attached to the outer surface of the upper pump plate of the impeller.
  • the impeller may additionally comprise a lower ring plate, which is formed near the outer circumference of the lower pump plate and is attached to the outer surface of the lower pump plate of the impeller.
  • the impeller may have an upper ring plate or a lower ring plate or both. Thereby reducing the gap between a pressure bushing and/or a pressure wall, respectively.
  • a pressure wall for a centrifugal pump for fluid having substantially the shape of a disc, the disc-shaped pressure wall having a central axis, the pressure wall comprising: a top surface, and a bottom surface opposing the top surface, wherein the top surface includes an inner surface section and an outer surface section, wherein the inner surface section extends radially from the central axis and is recessed to form a central recess; and wherein the outer surface section includes an inner circumferential edge portion and an outer circumferential edge portion, wherein the inner circumferential edge portion is located closer to the central axis than the outer circumferential edge portion, and wherein the outer circumferential edge portion is located higher than the inner circumferential edge portion with respect to a plane perpendicular to the central axis and passing through the inner circumferential edge portion.
  • the pressure wall further comprises a central through hole extending at least substantially along the central axis for bearing an impeller of the pump.
  • the height of the outer surface section measured from the inner circumferential edge portion to the outer circumferential edge portion increases in the direction perpendicular to the central axis of the pressure wall, preferably increases steadily.
  • the outer surface section is inclined towards the central axis of the pressure wall.
  • an inclination angle formed between the outer surface section and the plane perpendicular to the central axis is larger than 0° and less than or equal to 30°, preferably less than or equal to 20°, and more preferably less than or equal to 10°.
  • the outer surface section has a concave shape extending substantially around the entire circumference of the outer surface section. According to this, the fluid dynamics of the fluid directed to a heating unit are enhanced even more.
  • the outer surface section further has a helical shape extending substantially in the direction of the central axis of the pressure wall.
  • the helical shape extending substantially around the entire circumference of the outer surface section. Due to this, fluid flow in the direction of the outlet of the pump is enhanced.
  • the helical shape of the outer surface section extends over a major portion of the circumference of the outer surface section with the remaining portion connecting the end portions of the outer surface section together.
  • the pressure wall is a deep-drawn part. According to this, pressure wall is easy to manufacture, while keeping producing costs low.
  • the pressure wall is preferably made of a mold-able plastic part, such as a polypropylene (PP), a thermoset resin, a printed part, etc.
  • the pressure wall is made of a metal, preferably a corrosion-resistant metal, such as stainless steel or high-alloy steel.
  • the bottom surface is recessed to form a chamber for receiving a rotor of the motor of the pump.
  • the bottom surface comprises an outer circumferential edge to connect with a casing portion of the pump.
  • the central recess has a cylindrical shape which substantially matches the outer contour of an impeller.
  • a pump in particular for domestic appliances such as dishwashers, comprising: a pumping chamber including a central axial fluid inlet and a tangential fluid outlet, a heating unit for heating the fluid, an impeller for conveying fluid, wherein the impeller rotating within the pumping chamber, a motor for driving the impeller, and the pressure wall for deflecting the fluid flowing out of the impeller towards the heating unit of the pump.
  • a pressure bushing for a centrifugal pump for fluid having a substantially cylindrical shape, and comprising at least: a bottom portion, an outer side portion, and an inner side portion opposing the outer side portion and having an inner circumference surface, wherein the inner circumference surface of the inner side portion tapers at least partially towards the bottom portion of the pressure bushing.
  • the inner circumference surface of the inner side portion tapers towards the bottom portion by the method of tensile triangles. According to this, fluid dynamics of fluid flow can be enhanced. Thus, efficiency can be improved.
  • the resulting edges of the tensile triangles are rounded. Due to this, discontinuities in the fluid flow can be suppressed.
  • the cross-section of the inner side portion of the pressure bushing is be defined by at least one tensile triangle, preferably by at least three tensile triangles.
  • the pressure bushing further comprises a pressure ring, wherein the pressure ring is attached to the outer circumference of the bottom portion of the pressure bushing. Due to this, it is possible to generate fluid flows which are directed towards the heating unit. Thus, the efficiency of the heating-up process can be enhanced.
  • the pressure ring is configured to protrude over an upper pump plate of an impeller included in the pump.
  • the outer side portion comprises an aligning element, preferably a circumferentially extending ring for at least aligning the pressure bushing to a casing portion of the pump.
  • the pressure bushing is a mold-able plastic part, such as polypropylene, a thermoset resin or a printed part. Moreover, the pressure bushing may be a deep-drawn part.
  • the pressure bushing is made of a metal, preferably a corrosion-resistant metal, such as stainless steel or high-alloy steel.
  • the pressure ring comprises an end portion which has a phase, wherein the phase preferably has a phase angle of approximate 45°.
  • the pressure bushing is made of one piece.
  • a pump in particular for domestic appliances such as dishwashers, comprising: a pumping chamber including a central axial fluid inlet and a tangential fluid outlet, an impeller for conveying fluid, wherein the impeller rotating within the pumping chamber, a motor for driving the impeller, and a pressure bushing for conveying fluid to the impeller.
  • the pump further comprises a heating unit for heating the fluid.
  • a gap between the pressure bushing and the impeller is smaller than 5 mm, preferably smaller than 3 mm, and more preferably smaller than 2 mm.
  • the gap between the pressure bushing and the impeller is substantially constant over respective opposite outer surfaces.
  • Fig. 1a depicts a perspective view of an impeller 10 according to the state of art.
  • Impeller 10 includes a top plate 20 having a central opening and an opposing bottom plate 30, wherein vertical aligned blades 40 are arranged therebetween.
  • a rotor shaft (not shown) is coupled to a central recess of bottom plate 30 to rotate impeller 10 about its rotational axis.
  • Blades 40 are curved in a direction perpendicular to the rotational axis of impeller 10 to form a C-shape, seen from a top sectional view of Fig. 1b , wherein blades 40 extend from the center to an outer circumference of top plate 20 and bottom plate 30, respectively.
  • fluid enters impeller 10 at the central opening flows through an interior formed by top plate 20 and bottom plate 30, and out in the direction perpendicular to the rotational axis of impeller 10 at the outer circumference of top plate 20 and bottom plate 30.
  • blades 40 are curved to form a C-shape.
  • a respective sub-blade 50 is arranged between two subsequently blades 40.
  • Fig. 2a shows a perspective view of an impeller 100 according to an embodiment of the present invention.
  • Impeller 100 for a fluid pump comprises a lower pump plate 110 having at least one coupling section 112 configured to be coupled to a rotor shaft RS for driving impeller 100 about its rotational axis R.
  • Impeller 100 further comprises an upper pump plate 120 opposing lower pump plate 110 and having a central opening 122 for providing an inlet for a fluid to be pumped.
  • a plurality of blades 130 are arranged between lower pump plate 110 and upper pump plate 120.
  • Lower pump plate 110 and upper pump plate 120 both have an outer circumference forming an outlet for the pumped fluid. According to this, the fluid flows in a fluid flow direction F from the fluid inlet through a pump interior formed by lower 110 and upper pump plate 120, and out at the fluid outlet.
  • Each of blades 130 has a suction surface 131, a pressure surface 132 opposing suction surface 131, side edges 133, 134, 135, 136 and a longitudinal axis extending at least substantially in fluid flow direction F: a first longitudinal side edge 133 of each blade 130 being attached to upper pump plate 120, a second longitudinal side edge 134 of each blade 130 opposing first longitudinal side edge 133, and being attached to lower pump plate 110, an inflow side edge 135 of each blade 130 being arranged at least substantially in the opposite direction of the fluid flow F, and an outflow side edge 136 opposing inflow side edge 135, and being arranged at least substantially in the direction of fluid flow F.
  • an angle is formed between outflow side edge 136 and lower pump plate 110, which is an acute angle.
  • An acute angle is an angle that measures between 90° and 0°, meaning it is smaller than a right angle (an "L" shape) but has at least some space between the two lines that form it. In this particular case, the angle between outflow side edge 136 and lower pump plate 110 is approximately 60°.
  • lower pump plate 110 comprises a cross-section which corresponds to a hat-like trapezoid with rounded edges, and wherein the hat-like trapezoid with rounded edges corresponds to a bell-like trapezoid with rounded edges.
  • Upper pump plate 120 comprises a cross-section which decreases steadily, in particular exponentially, from the inside to the outside.
  • each blade 130 of impeller 100 is circularly arranged in regular intervals from each other between lower pump plate 110 and upper pump plate 120.
  • impeller 100 includes five blades 130.
  • impeller 100 further comprises a plurality of sub-blades 140, i.e. five in this particular embodiment, arranged between lower pump plate 110 and upper pump plate 120, and extending from the outer circumference of lower pump plate 110 and upper pump plate 120 to the interior formed by lower pump plate 110 and upper pump plate 120.
  • impeller 100 comprises five blades 130 and five corresponding sub-blades 140.
  • the radial extension of sub-blades 140 is less than the radial extension of blades 130.
  • Sub-blades 140 are used to increase the pressure inside impeller 100 and thereby enhancing efficiency of a pump including impeller 100.
  • Each sub-blade 140 opposing two blades 130 and is associated to a respective blade 130, wherein a distance between a sub-blade 140 to an associated blade 130 is different to another opposing blade 130. Further, each blade 130 is torqued or rather twisted in the direction perpendicular to rotational axis R of impeller 100. Additionally, each blade 130 and sub-blade 140 of impeller 100 is tapered towards respective inflow side edge 135.
  • each blade 130 formed between first longitudinal side edge 133 and inflow side edge 135, extends at least partially into central opening 122 of upper pump plate 120, thereby upper section 137 of each blade 130 has a substantially frustum shape with a rounded outer circumference.
  • each blade 130 measured from first longitudinal side edge 133 to second longitudinal side edge 134 decreases steadily in the direction perpendicular to rotational axis R of impeller 100 form the inside to the outside. Furthermore, each blade 130 terminates at the outer circumference of lower pump plate 110 and upper pump plate 120.
  • Fig. 3a depicts a perspective view of an impeller 200 according to a further embodiment of the present invention.
  • Fig. 3b is a sectional side view cut along a plane parallel to rotational axis R of impeller 200 of Fig. 3a .
  • Impeller 200 for a fluid pump P comprises a lower pump plate 210 having at least one coupling section 212 configured to be coupled to a rotor shaft RS (not shown) for driving impeller 200 about its rotational axis R.
  • Impeller 200 further comprises an upper pump plate 220 opposing lower pump plate 210 and having a central opening 222 for providing an inlet for a fluid to be pumped, and a plurality of blades 230 arranged between lower pump plate 210 and upper pump plate 220.
  • Lower pump plate 210 and upper pump plate 220 both have an outer circumference forming an outlet for the pumped fluid. According to this, the fluid flows in a fluid flow direction F from the fluid inlet through a pump interior formed by lower pump plate 210 and upper pump plate 220, and out at the fluid outlet.
  • FIGs. 4a and 4b show different perspective views of a blade 230 used in impeller 200 depicted in Figs. 3a to 3d .
  • Each of blades 230 has a suction surface 231, a pressure surface 232 opposing suction surface 231, side edges 233, 234, 235, 236 and a longitudinal axis extending at least substantially in fluid flow direction F: a first longitudinal side edge 233 of each blade 230 being attached to upper pump plate 220, a second longitudinal side edge 234 of each blade 230 opposing first longitudinal side edge 233, and being attached to lower pump plate 210, an inflow side edge 235 of each blade 230 being arranged at least substantially in the opposite direction of the fluid flow F, and an outflow side edge 236 opposing inflow side edge 235, and being arranged at least substantially in the direction of the fluid flow F.
  • an angle is formed between outflow side edge 236 and lower pump plate 210, which is an acute angle.
  • the angle between outflow side edge 236 and lower pump plate 210 is approximately 60°.
  • suction surface 231 of each blade 230 has at least partially a convex curvature extending at least substantially in the direction of rotational axis R of impeller 200.
  • pressure surface 232 of each blade 230 has at least partially a concave curvature extending at least substantially in the direction of rotational axis R of impeller 200.
  • the convex and/or concave curvatures extend substantially along the entire surface of each blade 230 in direction of the longitudinal axis extending at least substantially in fluid flow direction F.
  • inflow side edge 235 and outflow side edge 236 of each blade 230 is curved substantially in the direction of rotational axis R of impeller 200.
  • lower pump plate 210 comprises a cross-section which corresponds to a hat-like trapezoid with rounded edges, and wherein the hat-like trapezoid with rounded edges corresponds to a bell-like trapezoid with rounded edges.
  • Upper pump plate 220 comprises a cross-section which decreases steadily, in particular exponentially, from the inside to the outside.
  • Fig. 3c is a sectional top view cut along a plane perpendicular to rotational axis R of impeller 200 of Fig. 3a .
  • Each blade 230 is torqued in the direction perpendicular to rotational axis R of impeller 200. Additionally, each blade 230 and sub-blade 240 of impeller 200 is tapered towards the respective inflow side edge 235.
  • Fig. 3d is a perspective sectional view cut along a plane parallel to rotational axis R of impeller 200 of Fig. 3a , inflow side edge 235 of each blade 230 is curved substantially in the direction of rotational axis R of impeller 200.
  • Fig. 5a shows a perspective view of an impeller 300 according to another embodiment of the present invention, wherein Fig. 5b is a corresponding sectional side view cut along a plane parallel to rotational axis R of impeller 300 of Fig. 5a .
  • each blade 330 and each sub-blade 340 comprises a cross-section which has a wave-form or rather a fin-form, wherein the wave-form includes an upward portion and a downward portion.
  • Fig. 6a depicts a perspective view of an impeller 400 according to a further embodiment of the present invention.
  • Fig. 6b is a sectional side view cut along a plane parallel to rotational axis R of impeller 400 of Fig. 6a .
  • impeller 400 shown in Figs. 6a and 6b mostly corresponds to that depicted in Figs. 5a to 5b with the exception that the outer circumference of lower pump plate 410 is larger than the outer circumference of upper pump plate 420. This increases the outlet surface of the fluid outlet.
  • Fig. 7a depicts a perspective view of a pump P according to an embodiment of the present invention
  • Fig. 7b is a perspective sectional view cut along a plane parallel to rotational axis R of impeller of pump P of Fig. 7a .
  • pump P comprises a pumping chamber including a central axial fluid inlet and a tangential fluid outlet, and an impeller 10; 100; 200; 300; 400 for conveying fluid. Impeller 10; 100; 200; 300; 400 rotating within the pumping chamber. Pump P further comprises a motor (not shown) including a rotor shaft RS, wherein the rotor shaft RS is attached to the at least one coupling section 112; 212; 312; 412 of impeller 10; 100; 200; 300; 400.
  • a heating unit H is arranged near the inner circumference of pumping chamber for heating the fluid.
  • pump P further includes a pressure wall 500 arranged underneath impeller 10; 100; 200; 300; 400.
  • Pressure wall 500 is described in more detail with respect to Figs. 8a, 8b , 9a and 9b below.
  • Pump P further comprises a pressure bushing 600 arranged on top of central opening 122; 222; 322; 422 of upper pump plate 20; 120; 220; 320; 420 of impeller 100; 200; 300; 400, and which is used for guiding fluid towards inlet of impeller 10; 100; 200; 300; 400.
  • Pressure bushing 600 is described in detail with respect to Figs. 10a and 10b below. Pressure wall 500 and pressure bushing 600 can be used with any conventional pump.
  • Fig. 8a depicts a perspective view of a pressure wall 500 according to an embodiment of the present invention.
  • Fig. 8b is a perspective sectional side view cut along a plane parallel to the central axis A of pressure wall 500 of Fig. 8a .
  • pressure wall 500 is arranged underneath impeller 10; 100; 200; 300; 400 of pump P.
  • Pressure wall 500 is used to guide fluid conveyed out of impeller 10; 100; 200; 300; 400 to an outlet port of pump P.
  • pressure wall 500 has substantially the shape of a disc.
  • Disc-shaped pressure wall 500 has a central axis A.
  • Pressure wall 500 comprises a top surface 510, and a bottom surface 520 opposing top surface 510, wherein top surface 510 includes an inner surface section 512 and an outer surface section 514.
  • Inner surface section 512 extends radially from central axis A and is recessed to form a central recess 516.
  • Outer surface section 514 includes an inner circumferential edge portion 518 and an outer circumferential edge portion 519, wherein inner circumferential edge portion 518 is located closer to central axis A than outer circumferential edge portion 519.
  • Outer circumferential edge portion 519 is located higher than the inner circumferential edge portion 518 with respect to a plane perpendicular to central axis A and passing through inner circumferential edge portion 518.
  • pressure wall 500 comprises a cylindrical side surface 530.
  • Pressure wall 500 further comprises a central through hole 540 extending at least substantially along central axis A for bearing an impeller 10; 100; 200; 300; 400 of pump P.
  • the height of outer surface section 514 measured from inner circumferential edge portion 518 to outer circumferential edge portion 519 increases in the direction perpendicular to central axis A of pressure wall 500.
  • Outer surface section 514 is inclined towards central axis A of pressure wall 500.
  • outer surface section 514 has a concave shape extending substantially around the entire circumference of outer surface section 514.
  • Fig. 9a is a perspective view of a pressure wall 500 according to a further embodiment of the present invention.
  • Fig. 9b is a sectional side view cut along a plane parallel to the central axis A of pressure wall 500 of Fig. 9a .
  • pressure wall 500 shown in Figs. 9a and 9b mostly corresponds to that depicted in Figs. 8a and 8b with the exception that outer surface section 514 of top surface 510 of pressure wall 500 has in addition to the concave shape a helical shape which extends in direction towards central axis A of pressure wall 500. Helical shape extends almost entirely around the entire circumference of outer surface section 514 of top surface 510 of pressure wall 500.
  • Fig. 10a shows a perspective view of a pressure bushing 600 according to an embodiment of the present invention.
  • Fig. 10b depicts a sectional side view cut along a plane parallel to the central axis A of pressure bushing 600 of Fig. 10a .
  • pressure bushing 600 comprises a bottom portion 610, an outer side portion 620 and an inner side portion 630.
  • Bottom portion 610 is configured to match the contour of upper pump plate 20; 120; 220; 320; 420 of impeller 10; 100; 200; 300; 400 and can be attached thereto. This is particularly shown in pump P of Figs. 7a and 7b .
  • Inner side portion 630 of pressure bushing 600 has an inner circumference, which tapers towards bottom portion 610 of pressure bushing 600, i.e. towards upper pump plate 20; 120; 220; 320; 420 of impeller 10; 100; 200; 300; 400 of pump P in an assembled configuration.
  • inner circumference of inner side portion 630 of pressure bushing 600 tapers towards bottom portion 610 by the method of tensile triangles, with the resulting edges rounded.
  • the cross-section of inner side portion 630 of pressure bushing 600 is defined by three tensile triangles 640.
  • Fig. 11 depicts a sectional side view of an impeller 200 cut along a plane parallel to rotational axis R of impeller 200 according to a further embodiment of the present invention.
  • the embodiment of impeller 200 shown in Fig. 11 mostly corresponds to that depicted in Figs. 3a to 3d with the exception that a circumferential upper ring plate 238 is formed near the outer circumference of upper pump plate 220 and a circumferential lower ring plate 238 is formed near the outer circumference of lower pump plate 210.
  • Ring plates 238, 239 are attached to the outer surfaces of pump plates 210, 220 of impeller 200, respectively.
  • Fig. 12 shows a sectional view of a pressure bushing 600 according to a further embodiment of the present invention.
  • the embodiment of pressure bushing 600 depicted in Fig. 12 mostly corresponds to that shown in Figs. 10a and 10b with the exception that bottom portion 610 further comprises a pressure ring 650 attached to the outer circumference of bottom portion 610 of pressure bushing 600.
  • Fig. 13 depicts a sectional view of a pump P according to another embodiment of the present invention including pressure bushing 600 of Fig. 12 .
  • pressure ring 650 protrudes over upper pump plate 220 of impeller 200 and thereby reduces the gap between pressure bushing 600 and impeller 200.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Geometry (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
EP21189275.7A 2021-08-03 2021-08-03 Roue de pompe à fluide et pompe comprenant ladite roue Withdrawn EP4130485A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP21189275.7A EP4130485A1 (fr) 2021-08-03 2021-08-03 Roue de pompe à fluide et pompe comprenant ladite roue
PCT/EP2022/071822 WO2023012219A1 (fr) 2021-08-03 2022-08-03 Roue à aubes pour pompe à fluide et pompe comprenant la roue à aubes

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP21189275.7A EP4130485A1 (fr) 2021-08-03 2021-08-03 Roue de pompe à fluide et pompe comprenant ladite roue

Publications (1)

Publication Number Publication Date
EP4130485A1 true EP4130485A1 (fr) 2023-02-08

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EP21189275.7A Withdrawn EP4130485A1 (fr) 2021-08-03 2021-08-03 Roue de pompe à fluide et pompe comprenant ladite roue

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EP (1) EP4130485A1 (fr)
WO (1) WO2023012219A1 (fr)

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5148803A (en) * 1974-10-23 1976-04-27 Susumu Terada Taabokikaino haneguruma
JPS59168297A (ja) * 1983-03-16 1984-09-21 Hitachi Ltd 溶接羽根車
SU1605035A1 (ru) * 1988-10-30 1990-11-07 Предприятие П/Я В-8534 Центробежный насос
DE102006023856A1 (de) 2006-05-19 2007-11-22 Aweco Appliance Systems Gmbh & Co. Kg Pumpvorrichtung mit einem Elektromotor zum Antreiben eines Pumpenrades
US20160025100A1 (en) * 2013-04-17 2016-01-28 Sulzer Management Ag Impeller for a centrifugal pump and centrifugal pump
US20160076551A1 (en) * 2013-06-13 2016-03-17 Mitsubishi Heavy Industries Compressor Corporation Impeller and fluid machine
CN111963477A (zh) * 2020-08-26 2020-11-20 安德里茨（中国）有限公司 陶瓷叶轮固定装置、陶瓷叶轮及其制造方法、拆卸方法

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5148803A (en) * 1974-10-23 1976-04-27 Susumu Terada Taabokikaino haneguruma
JPS59168297A (ja) * 1983-03-16 1984-09-21 Hitachi Ltd 溶接羽根車
SU1605035A1 (ru) * 1988-10-30 1990-11-07 Предприятие П/Я В-8534 Центробежный насос
DE102006023856A1 (de) 2006-05-19 2007-11-22 Aweco Appliance Systems Gmbh & Co. Kg Pumpvorrichtung mit einem Elektromotor zum Antreiben eines Pumpenrades
US20160025100A1 (en) * 2013-04-17 2016-01-28 Sulzer Management Ag Impeller for a centrifugal pump and centrifugal pump
US20160076551A1 (en) * 2013-06-13 2016-03-17 Mitsubishi Heavy Industries Compressor Corporation Impeller and fluid machine
CN111963477A (zh) * 2020-08-26 2020-11-20 安德里茨（中国）有限公司 陶瓷叶轮固定装置、陶瓷叶轮及其制造方法、拆卸方法

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