EP2058525B1 - Rad für ein Radialgebläse und Radialgebläse - Google Patents

Rad für ein Radialgebläse und Radialgebläse Download PDF

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Publication number
EP2058525B1
EP2058525B1 EP07425710A EP07425710A EP2058525B1 EP 2058525 B1 EP2058525 B1 EP 2058525B1 EP 07425710 A EP07425710 A EP 07425710A EP 07425710 A EP07425710 A EP 07425710A EP 2058525 B1 EP2058525 B1 EP 2058525B1
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EP
European Patent Office
Prior art keywords
impeller
main
blade
blades
auxiliary
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EP07425710A
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English (en)
French (fr)
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EP2058525A1 (de
Inventor
Maurizio Achille Abate
Mauro Castello
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Elica SpA
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Elica SpA
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Publication date
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Priority to EP07425710A priority Critical patent/EP2058525B1/de
Priority to DE602007006209T priority patent/DE602007006209D1/de
Priority to AT07425710T priority patent/ATE466195T1/de
Priority to RU2008144614/06A priority patent/RU2492363C2/ru
Publication of EP2058525A1 publication Critical patent/EP2058525A1/de
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Publication of EP2058525B1 publication Critical patent/EP2058525B1/de
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    • 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
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
    • F04D29/281—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for fans or blowers
    • 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
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
    • F04D29/30—Vanes

Definitions

  • the objects of the present invention are an impeller for a radial fan and a radial fan provided with such impeller.
  • Radial fans in particular fans intended to transfer air and/or gas (frequently in the form of a mixture thereof) to boilers, such as, for example, condensation boilers, comprise a housing provided with a suction port and a air exhausting port. Inside the housing, an impeller is provided which is able to rotate about a rotation axis. The air enters the housing through the suction port in the axial direction, it passes through the impeller, and it is discharged therefrom in the radial direction in a spiral portion of the housing, from where the air reaches the exhausting port.
  • the impeller is provided with a plurality of blades arranged about the rotation axis of the impeller having an arch-shaped profile in the transversal direction to the rotation axis.
  • Radial fans should be capable of providing suitable lifts in well-defined capacity intervals (so-called "working curves") in order to ensure the proper functioning, for example, of the condensation boiler which they are connected to.
  • a further particularly felt need which the research in the field of radial fans devotes considerable efforts to, is to achieve dimension decrements without a performance worsening.
  • a further most felt need is that the energy consumption associated with the impeller operation, which is usually actuated by an electric motor, is reduced.
  • the object of the present invention is to provide an impeller for a radial fan and a radial fan which allow obtaining efficient lift-capacity curves, in particular which are suitable for the operation of condensation boilers, such as not to require undue power consumption for the impeller actuation and which, in the whole, have reduced dimensions.
  • Fig. 1 is an exploded perspective view of a radial fan according to the invention
  • Fig. 2 is a perspective view of an impeller according to the invention.
  • Fig. 3 is a perspective view from a different angle of the impeller in Fig. 2 ;
  • Fig. 4 is a side view of the impeller in Fig. 2 ;
  • Fig. 5 is an enlarged view of the detail A of the impeller in Fig. 4 ;
  • Fig. 6 is an enlarged view of the detail B of the impeller in Fig. 4 ;
  • Fig. 7 is a further side view of the impeller in Fig. 2 ;
  • Fig. 8 a further side view of the impeller in Fig. 2 ;
  • Fig. 9 is a sectional view, according to the IX-IX line, of the impeller in Fig. 8 ;
  • Fig. 10 is a perspective view of a component of the radial fan in Fig. 1 ;
  • Fig. 11 is a further perspective view of the component in Fig. 10 ;
  • Fig. 12 is a side view of the component in Fig. 10 ;
  • Fig. 13 is a sectional view, according to the XIII-XIII line, of the component in Fig. 12 ;
  • Fig. 14 is a further side view of the component in Fig. 10 ;
  • Fig. 15 is a further side view of the component in Fig. 10 ;
  • Fig. 16 is a sectional view, according to the XVI-XVI line, of the component in Fig. 15 ;
  • Fig. 17 is a perspective view of a further component of the radial fan in Fig. 1 ;
  • Fig. 18 is a further perspective view of the component in Fig. 17 ;
  • Fig. 19 is a side view of the component in Fig. 17 ;
  • Fig. 20 is a further side view of the component in Fig. 17 ;
  • Fig. 21 is a sectional view, according to the XXI-XXI line, of the component in Fig. 20 ;
  • Fig. 22 is a further side view of the component in Fig. 17 ;
  • Fig. 23 is an exploded, perspective view of an impeller according to a further embodiment of the invention.
  • Fig. 24 is a perspective view of an impeller according to a further embodiment of the invention.
  • a radial fan is indicated by the reference numeral 1.
  • the fan 1 is, for example, adapted to convey air and/or gas (also as a mixture thereof) towards a burner, a boiler, or a general heating system.
  • the fan 1 is particularly adapted to the conveyance of air and/or gas towards a condensation boiler.
  • the fan 1 comprises an impeller 2 able to rotate about a rotation axis A, in particular inside a fan housing 3.
  • the terms “axial” and “radial” refer to the rotation axis A of the impeller 2, unless otherwise noted.
  • the housing 3 preferably comprises two mutually connectable, separate parts, for example a half-shell 4 which defines an impeller space 6 adapted to receive the impeller 2 therein, and a lid 5 adapted to close the impeller space 6.
  • the half-shell 4 and the lid 5 can be mutually connected, for example, through threaded couplers 7.
  • the lid 5 can further comprise a projecting portion 5' ( Figures 18-19 ) adapted to shape-fit into the impeller space 6 defined by the half-shell 4, which advantageously is essentially complementary thereto.
  • the lid 5 is adapted to support a preferably electric motor 8 intended to rotate the impeller 2 through a shaft 9 thereof which, in the assembled fan 1 condition, is coaxial to the rotation axis A.
  • the motor 8 can be connected to the lid 5 through an intermediate support 10 prearranged for the connection to the lid 5, for example through screws 11 to be inserted in corresponding screw seats 12 of the lid 2.
  • the screw seats 12 are arranged at constant angular distances along a circumference.
  • the screw seats 12 can be in a number of three and spaced at 120° apart one to the other.
  • the intermediate support 10 can be provided with as many radial brackets 15 correspondingly distributed to the screw seats 12 of the lid 10.
  • the fan 1 can comprise vibration dampening means.
  • vibration dampening means comprise first dampeners 13 adapted to act between the intermediate support 10 and the lid 5, for example rubber members provided with an opening passing through the bore for the screws 11, so as to dampen the vibrations parallel to the rotation axis A.
  • the fan 1 can further comprise second dampeners 14, acting between the intermediate support 10 and the lid 5, thus oriented and shaped so as to dampen the vibrations which, from the motor 8, transfer to the housing 3 along radial directions.
  • the second dampeners 14, for example, rubber members, can be inserted in support brackets 16 formed by or connected to the lid 5, and preferably arranged along a circumference which is inside the circumference along which the screw seats 12 are arranged. Still more preferably, such support brackets 16 are in a number of three and arranged at 120° one to the other.
  • the second dampeners 14 can, for example, be laterally contacted to the intermediate support 10, so as to act in the radial direction between the latter and the support brackets 16.
  • the latter can comprise a covering member 17 which is connectable to the lid 5, for example, through screws 18.
  • a covering member 17 is preferably cup-shaped, so as to make the motor 8 not accessible, once the fan 1 is assembled.
  • the covering member 17 can act so as to protect both the motor 8 and one or more further auxiliary members 48, such as, for example, control logic circuits for the motor 8.
  • the lid 5 comprises a through opening 19.
  • the fan 1 comprises an air and/or gas suction port 20 and exhausting port 21.
  • the suction port 20 and the exhausting port 21 are formed in the half-shell 4 ( Figures 1 and 10-16 ).
  • the suction port 20 is preferably laterally arranged on the half-shell 4 and it is so shaped that the entering air and/or gas enter the impeller space 6 and reach the impeller 2 along an essentially axial direction.
  • the exhausting port 21 is preferably formed at an end 23 of an exhausting portion 22 of the half-shell 4 which extends in a direction which is essentially tangential to the housing 3, so that air and/or gas discharged by the impeller 2 may circulate in the impeller space 6 according to essentially tangential flow lines, and are discharged by the fan 1 through the exhausting port 21 without being subjected to undue deviations of their motion.
  • a flange 24 can be provided, adapted to connect the fan 1 to outer support members (not shown in the Figures), for example, through threaded couplers.
  • the impeller 2 comprises a plurality of main blades 25 sequentially arranged about the rotation axis A ( Figures 2-9 ).
  • Each of such main blades 25 has a radially innermost inlet end 32 and a radially outermost outlet end 33.
  • the inlet end 32 has the function of sucking and entrapping the air and/or gas coming from the suction port 20 in the axial direction
  • the outlet end 34 has the function of guiding the air and/or gas discharged by the impeller 2 to the impeller space 6 of the housing 3.
  • Each of the main blades 25 comprises a concave main blade first surface 26 and a convex main blade second surface 27 opposite the main blade first surface 26. In this way, each of the main blades 25 has an essentially arc-shape. Furthermore, the main blade second surface 27 of each of the main blades 25 is facing the main blade first surface 26 of the next main blade. In this way, a flow passage 28 for air and/or gas conveyance between a radially inner position and a radially outer position of the impeller 1 is formed between two successive main blades of a pair of main blades.
  • the impeller 2 rotating under the effect of the actuation by the motor 8, sucks the air and/or gas from the suction port 20 of the housing 3, coaxial to the impeller 2, and conveys them under the effect of the impeller rotation into the flow passages 28 defined by the main blades 25, finally radially discharging them outside the impeller 2 in the impeller space 6.
  • the main blades 25 are shaped so as to optimize the inner fluid dynamics of the impeller, hence the overall performance of the fan 1.
  • main blade first surfaces 26 of the main blades 25 are so shaped as to define main blade arcs PP which comprise a main blade first circle arc PP1, a main blade second circle arc PP2, a main blade third circle arc PP3, and a main blade fourth circle arc PP4, radially arranged from the inside to the outside of the impeller 2 ( Fig. 5 ).
  • each of such circle arcs PP1, PP2, PP3, PP4 has its own radius of curvature, in particular the first circle arc PP1 has a first radius of curvature R1, the second circle arc PP2 has a second radius of curvature R2, the third circle arc PP3 has a third radius of curvature R3, and the fourth circle arc PP4 has a fourth radius of curvature R4.
  • the main blade radii of curvature have ratios in the following ranges:
  • the above-mentioned ratios between the main blade radii of curvature have approximately the following ratios, ranging within the previously noted intervals:
  • the main blade arcs PP are advantageously without discontinuity points.
  • the adjacent circle arcs have the same slope or, in mathematical terms, have the same first derivative.
  • the impeller 2 comprises a plurality of auxiliary blades 29 preferably having an extension which is smaller than the main blades 25 extension, also arranged about the impeller 2 rotation axis.
  • the auxiliary blades 29 are individually or in groups arranged between a first and a second main blades of a pair of main blades 25.
  • the main blades 25 and the auxiliary blades 29 are alternating one to the others, so that in each of the flow passages 28 a single one of the auxiliary blades 29 is provided for.
  • Each of the auxiliary blades 29 has a radially inner inlet end 34 and a radially outer outlet end 35. Furthermore, each of the auxiliary blades 29 comprises a concave auxiliary blade first surface 30 and a convex auxiliary blade second surface 31, opposite the auxiliary blade first surface 30 of the same auxiliary blade 29 ( Fig. 6 ).
  • the auxiliary blade first surface 30 of each of the auxiliary blades 29 is facing the main blade second surface 27 of a first one of the main blades 25 between which the auxiliary blade 29 is arranged, and the auxiliary blade second surface 31 of each of the auxiliary blades 29 is facing the main blade first surface 26 of a second one of the main blades 25 between which the auxiliary blade 29 is arranged.
  • auxiliary blade first surfaces 30 of each of the auxiliary blades 29 define auxiliary blade arcs PS which comprise a first circle arc PS1, a second circle arc PS2, and a third circle arc PS3, radially arranged from the inside to the outside of the impeller 2.
  • auxiliary blade circle arcs PS1, PS2, PS3 has its own radius of curvature, in particular the first circle arc PS1 has a first radius of curvature r1, the second circle arc PS2 has a second radius of curvature r2, and the third circle arc PS3 has a third radius of curvature r3.
  • the auxiliary blade radii of curvature have ratios which are advantageously in the following ranges:
  • the auxiliary blade radii of curvature have the following dimensional ratios, ranging within the above-mentioned intervals:
  • the auxiliary blade arcs PS also are without discontinuity points.
  • the air and/or gas turbulences are reduced when passing through the flow passages 28; in addition, in this way the overall head losses in the fan 1 during its functioning are also reduced.
  • the main blades 25 and the auxiliary blades 29 have mutual dimensional ratios specifically designed in order to achieve a high overall performance for the fan 1.
  • the first auxiliary blade radius of curvature r1 and the first main blade radius curvature R1 have a ratio r1/R1 ranging within 1.2-1.3.
  • such ratio r1/R1 is equal to about 1.25.
  • the main blades 25 have a main blade thickness s pp defined between the main blade first surface 26 and the main blade second surface 27, and the auxiliary blades 29 have an auxiliary blade thickness s ps defined between the auxiliary blade first surface 30 and the auxiliary blade second surface 31 ( Figures 5 and 6 ).
  • the first main blade radius R1 and the main blade thickness s pp have a ratio R1/s pp ranging within 18-21, preferably equal to about 19.5.
  • the first main blade radius r1 and the auxiliary blade thickness s ps have a ratio r1/s ps ranging within 23-26, preferably equal to about 24.32.
  • the main blade thickness s pp and the auxiliary blade thickness s ps are constant and essentially equal one to the other, so as to simplify the impeller 2 working operations.
  • the main blades and/or auxiliary blades thicknesses are evaluated in one of their axial ends. Due to the working operations of the impeller, the blades can have a gradually variable thickness between such two axial ends (for example, in order to make their detachment from the moulds easier). In such a case, the smallest thicknesses of the blades are taken as main blade s pp and auxiliary blade s ps thicknesses.
  • the blades In order to ensure an efficient air and/or gas conveyance through the impeller 2, as well as reduced power consumptions by the motor 8 actuating the impeller 2, it is important that the blades, as well as the above-described shape, also have a suitable spatial arrangement inside the impeller, as well as a suitable orientation at the inlet and outlet ends thereof, where the air and/or gas are respectively suctioned and discharged.
  • T outpp which is tangential to the main blade arc PP
  • R outpp which connects such outlet end 33 to the impeller center, that is to the rotation axis A.
  • T outpp and R outpp define a main blade exiting angle ⁇ outpp which, advantageously, ranges between 45° and 55°, and which is preferably equal to about 50.4°.
  • T inpp which is tangential to the main blade arc PP
  • R inpp which connects such inlet end 32 to the rotation axis A.
  • T inpp and R inpp individuate a main blade entering angle ⁇ inpp which, advantageously, ranges between 0° and 15°, and which is preferably equal to about 12.9°.
  • the auxiliary blade exiting angle ⁇ outps can range between 45° and 55°, and it is preferably equal to about 50.7°.
  • the auxiliary blade entering angle ⁇ inps can range between 25° and 35°, and it is preferably equal to about 30.1°.
  • the auxiliary blade enclosing angle ⁇ ps can range between 15° and 20°, and it is preferably equal to about 17.8°.
  • the outlet ends 33 of the main blades 25 are arranged so as to define an impeller outer circumference which essentially delimits the maximum radial dimensions of the impeller.
  • the inlet ends 32 of the main blades 25 are arranged so as to define a main blades inner circumference.
  • the impeller outer circumference and the main blades inner circumference have an impeller diameter D max and a main blades inner diameter d ipp ( Fig. 8 ), respectively, which, advantageously, have a dimensional ratio D max /d ipp ranging within 2-3.5, and which is preferably equal to about 2.78.
  • the impeller 2 has an impeller axial height h ext ( Fig. 7 ).
  • the impeller diameter D max and the impeller axial height h ext have a ratio D max /h ext ranging within 6-9, and which is preferably equal to about 7.37.
  • the outlet ends 35 of the auxiliary blades are also arranged along the impeller outer circumference ( Fig. 4 ). Furthermore, the inlet ends 34 thereof are arranged so as to define an auxiliary blades inner circumference with an auxiliary blades inner diameter d ips .
  • the impeller diameter D max and the auxiliary blades inner diameter d ips have a ratio D max /d ips ranging within 1.2-1.6, preferably equal to about 1.43.
  • the impeller diameter D max and the first main blade radius of curvature R1 have a ratio D max /R1 ranging within 4-5, preferably equal to 4.4.
  • the impeller 2 provided with the blades having the previously-described features can be constructively produced according to different conformations.
  • the impeller 2 comprises a first 36 and a second 37 separate and connectable support members.
  • the first support member 36 is intended to be connected to the motor 8 shaft 9 for the impeller 2 actuation.
  • the second support member 37 is located opposite the first support member 36 and comprises an opening 38 which is designed, once the fan is assembled, to be arranged in a position which corresponds to the suction port 20 of the housing 3, so as to axially suck the air and/or gas from outside the fan during the impeller 2 rotational movement.
  • the first 36 and the second 37 support members enclose, on two axially opposing sides, the flow passages 28 defined by the blades, thereby forcing the air and/or gas to pass therein.
  • the main and/or auxiliary blades can be made in a single piece with the second support member 37 (as shown in Fig. 23 ).
  • the blades can be made in a single piece with the first support member 36 (such solution is not shown in the Figures).
  • first support member 36, the second support member 37, and the main 25 and/or second 29 blades are mutually separate and connectable (in this regard, reference is to be made, for example, to Fig. 24 , in which an impeller 2 is shown provided only with main blades 25).
  • first 36 and the second 37 support members can comprise connection seats 39 intended to receive connection means which are either connectable to the blades or formed in a single piece therewith.
  • first support member 36, the second support member 37, and the main and/or second blades are made as one piece ( Figures 2-9 ), for example by means of a moulding process.
  • the first support member 36 and the second support member 37 advantageously have essentially complementary shapes. Furthermore, the first support member 36 and the second support member 37 are arranged so that the projection of the first support member 36 on the second support member 37 along the impeller A rotation axis is correspondent or inner to the air and/or gas opening 38 of the second support member 37.
  • the second support member 37 may be of a ring shape, the air and/or gas passage opening 38 having a circular shape, and the first support member 36 may be of a circular shape having dimensions which are equal to or smaller (preferably slightly smaller) than those of the opening 38.
  • suitable rakes are provided for one or more of the members which extend according to the rotation axis A.
  • a rake angle ⁇ is provided which ranges between 4 and 9°, preferably it is equal to 7° at the outlet ends 33 and 35 thereof, respectively (in this regard, see, for example, Fig. 9 ).
  • the rake angle ⁇ is so arranged that the impeller 2 radial dimensions are bigger on the first support member 36 side than on the second support member 37 side.
  • the first support member 36 and the second support member 37 are mutually connected through the main blades 25 ( Fig. 3 ).
  • the latter have their inlet ends 32 on the first support member 36 and comprise connection portions 40 in which the height thereof (in the impeller axial direction) gradually increases, from such inlet ends 32, radially towards the outside, until reaching the peak value at the second support member 37.
  • the main blades 25 radially extend to the outside along the second support member 37 to the outlet ends 33 thereof ( Fig. 2 ).
  • the outlet ends 33 of the main blades 25, which define the impeller circumference with diameter D max radially protrude in relation to the second support member 37, so as to suck air and/or gas possibly entrapped between the impeller 2 and the housing 3 during the fan 1 functioning ( Fig. 3 ).
  • a stiffening ring 41 can be provided on the impeller 2, also preferably made in a single piece with the impeller 2, connecting the outlet ends 33 of the main blades 25.
  • the stiffening ring 41 is located on the first support member 36 side.
  • the first support member 36 advantageously comprises a tubular portion 42 adapted to receive the motor 8 shaft 9 and which preferably extends parallel to the impeller rotation axis A.
  • the shaft 9 can be connected to the tubular portion 42 through locking means (not shown in the Figures) adapted to integrally connect rotationally and translationally the latter along the rotation axis A.
  • the first support member 36 of the impeller 2 comprises stiffening members adapted to oppose the impeller strains.
  • the first support member 36 can comprise one or more ribs 43 which radially extend starting from the tubular portion 42.
  • the ribs 43 are in a number of four and, still more preferably, are crosswise arranged and mutually spaced apart of about 90° (see, for example, Fig. 4 ).
  • the auxiliary blades 29 extend on the second support member 37 and, still more preferably, are also radially projecting to the outside of the latter, as the main blades 25 are, so as to co-operate in the suction of residual air and/or gas in the gap between the impeller 2 and the housing 3. Furthermore, the auxiliary blades inner circumference, along which the inlet ends 34 of the auxiliary blades 29 are arranged, is preferably located internally to the second support member 37, in a concentric manner thereto ( Fig. 4 ).
  • the impeller 2 in the single piece configuration is preferably made of a plastic material.
  • the impeller space 6 preferably has a configuration designed for coupling with the impeller 2 according to one or more of the embodiments described above.
  • the impeller space 6 of the housing transversally to the height H all thereof, therefore transversally to the impeller A rotation axis, has a transversal profile which comprises a main length 45 advantageously shaped as a plurality of successive housing circle arcs ( Fig. 12 ).
  • the impeller space 6 transversal profile can further comprise an exhausting length 46, in which the housing 3 extends in the exhausting portion 22, individuated by a reference angle ⁇ .
  • the main length 45 comprises four of the above-mentioned successive housing circle arcs, in particular a first CC1, a second CC2, a third CC3, and a fourth CC4 housing circle arcs having a first RC1, a second RC2, a third RC3, and a fourth RC4 housing radii of curvature, respectively.
  • Such housing circle arcs are arranged, preferably starting from the exhausting length 46, with a direction opposite to the rotation of the impeller 2 (in particular, with reference to the Fig. 12 , the housing circle arcs are arranged counter-clockwise, while the impeller is intended to rotate clockwise).
  • housing radii of curvature have ratios in the following ranges:
  • the above-mentioned ratios between the housing radii of curvature are approximately equal to:
  • D max /RC1 is equal to about 1.63.
  • the housing circle arcs are advantageously connected so that the main length 45 of the impeller space 6 transversal profile is essentially without discontinuity points.
  • the exhausting length 46 may have a width ⁇ ranging between 60° and 80°, preferably equal to about 70°.
  • the housing 3 comprises a conveyance tongue 47 adapted to convey air and/or gas exhausted by the impeller 2 towards the exhausting portion 22 and, therefrom, to the exhausting port 21 ( Figures 10-16 ).
  • conveyance tongue 47 preferably cantilevered formed in a single piece with the half-shell 4 of the housing 3, is located in the impeller space 6 at the exhausting length 46.
  • the conveyance tongue 47 advantageously extends along a tongue axis L which comprises an essentially rectilinear length, and which may optionally have slight curvatures at the two conveyance tongue ends, so as to partially enclose the impeller 2.
  • the conveyance tongue 47 has a gradually increasing section along the tongue extension axis L towards the exhausting port 21, so as to force the air and/or gas discharged by the impeller to run a circumferential path along all the impeller space, before reaching the exhausting portion 22.
  • such gradually increase of the conveyance tongue 47 section takes place in such a way that, proceeding along the tongue L extension axis towards the exhausting port 21, the conveyance tongue 47 width parallel to the rotation axis A increases towards the inner part of the impeller space 6 ( Fig. 13 ).
  • the housing 3, in particular the half-shell 4 and the lid 5, are preferably made in aluminium or an aluminium alloy.
  • the impeller 2 is provided with seventeen main blades 25 and seventeen auxiliary blades 29.
  • the auxiliary blades 25 and the auxiliary blades 29 are alternatively arranged about the impeller rotation axis A.
  • the impeller circumference has an impeller diameter D max equal to about 120 mm, along which the outlet ends 33 and 35 of the main blades 25 and the auxiliary blades 29 are arranged, respectively.
  • the impeller 2 further has an axial height h ext at the impeller circumference equal to about 16.28 mm.
  • the inlet end 32 of the main blades 25 are arranged according to a main blades inner circumference having a diameter d ipp of about 43.2 mm.
  • the four main blade circle arcs PP1, PP2, PP3, and PP4 have radii of curvature R1 equal to about 27.3 mm, R2 equal to about 29 mm, R3 equal to about 31.5 mm, and R4 equal to about 37.5 mm, respectively, and are mutually connected without discontinuity in the main blade arc PP profile.
  • the main blades 25 have a main blade enclosing angle ⁇ pp equal to about 22.8°, a main blade entering angle ⁇ inpp equal to about 12.9°, and a main blade exiting angle ⁇ outpp equal to about 50.4°.
  • the main blades 25 further have a thickness s pp essentially constant and equal to about 1.4 mm (to the axial end with smallest thickness).
  • the inlet ends 34 of the auxiliary blades 29 are arranged according to an auxiliary blades inner circumference having a diameter d ips of about 84 mm.
  • the three auxiliary blade circle arcs PS1, PS2, and PS3 have radii of curvature r1 equal to about 34.05 mm, r2 equal to about 37.8 mm, and r3 equal to about 36.75 mm, respectively, and are mutually connected without discontinuity in the auxiliary blade arc PS profile.
  • the auxiliary blades 29 have an enclosing angle of auxiliary blade ⁇ pa equal to about 17.8°, an auxiliary blade entering angle ⁇ inps equal to about 30.1°, and an auxiliary blade exiting angle ⁇ outps equal to about 50.7°.
  • the auxiliary blades further have a thickness s ps essentially constant and equal to about 1.4 mm (at the axial end with smallest thickness).
  • a housing 3 adapted to be coupled with an impeller of this kind has the impeller space 6 with an axial height H all of about 20.28 mm.
  • the impeller space transversal profile is so divided:
  • the four housing circle arcs have the following radii of curvature:
  • the fan overall dimensions essentially due to the impeller axial and radial dimensions, which dictate the housing axial and radial dimensions, are suitable for the applications which the fans according to the invention are intended to, in particular for air and/or gas supply to condensation boilers.

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

Claims (35)

  1. Gebläserad (2) für ein Radialgebläse (1), das zum Rotieren um eine Rotationsachse (A) angepasst ist und eine Vielzahl von Hauptschaufeln (25) aufweist, die sequentiell um die Rotationsachse (A) herum angeordnet sind und radial ganz innen Einlassenden (32) und radial ganz außen Auslassenden (33) aufweisen, wobei jede der Hauptschaufeln (25) eine konkave erste Hauptschaufeloberfläche (26) und eine konvexe zweite Hauptschaufeloberfläche (27) aufweist, die der ersten Hauptschaufeloberfläche (26) gegenüberliegt und der ersten Hauptschaufeloberfläche der nachfolgenden Hauptschaufel zugewandt ist, wobei die ersten Hauptschaufeloberflächen (26) Hauptschaufelbögen (PP) definieren, die einen ersten (PP1), einen zweiten (PP2), einen dritten (PP3) und einen vierten (PP4) Hauptschaufelkreisbogen aufweisen, die radial von der Innenseite zu der Außenseite des Gebläserads (2) angeordnet sind und jeweils einen ersten (R1), einen zweiten (R2), einen dritten (R3) und einen vierten (R4) Hauptschaufelkurvenradius aufweisen, dadurch gekennzeichnet, dass die Hauptschaufelkurvenradien (R1, R2, R3, R4) Quotienten in den folgenden Bereichen aufweisen: R2/R1 = 1-1,1; R3/R1 = 1,1-1,2; R4/R1 = 1,2-1,5.
  2. Gebläserad (2) nach dem vorhergehenden Anspruch, das eine Vielzahl von Hilfsschaufeln (29) aufweist, die individuell oder in Gruppen um die Rotationsachse (A) herum zwischen einem ersten und einem zweiten der Vielzahl von aufeinanderfolgenden Hauptschaufeln (25) angeordnet sind, und radial ganz innen Einlassenden (34) und radial ganz außen Auslassenden (35) aufweisen, wobei jede dieser Hilfsschaufeln (29) eine konkave erste Hilfsschaufeloberfläche (30) aufweist, die der zweiten Hauptschaufeloberfläche (27) der ersten Hauptschaufel zugewandt ist, und eine konvexe zweite Hilfsschaufeloberfläche (31), die der ersten Hilfsschaufeloberfläche (30) gegenüberliegt und der ersten Hauptschaufeloberfläche (26) der zweiten Hauptschaufel zugewandt ist, wobei die ersten Hauptschaufeloberflächen (30) Hilfsschaufelbögen (PS) definieren, die einen ersten (PS1), einen zweiten (PS2) und einen dritten (PS3) Hilfsschaufelkreisbogen aufweisen, die radial von der Innenseite zu der Außenseite des Gebläserads (2) angeordnet sind und jeweils einen ersten (r1), einen zweiten (r2) und einen dritten (r3) Hilfsschaufelkurvenradius aufweisen, wobei die Hilfsschaufelkurvenradien (r1, r2, r3) Quotienten in den folgenden Bereichen aufweisen: r ⁢ 2 / r ⁢ 1 = 1 , 08 - 1 , 15 ; r ⁢ 3 / r ⁢ 1 = 1 , 05 - 1 , 1.
    Figure imgb0001
  3. Gebläserad (2) nach dem vorhergehenden Anspruch, wobei der erste Hilfsschaufelkurvenradius (r1) und der erste Hauptschaufelkurvenradius (R1) einen Quotienten im folgenden Bereich aufweisen: r1/R1 = 1,2 - 1,3.
  4. Gebläserad (2) nach einem der vorhergehenden Ansprüche, wobei die Quotienten zwischen den Hauptschaufelkurvenradien (R1, R2, R3, R4) ungefähr gleich den folgenden Werten sind: R2/R1 = 1,06; R3/R1 = 1,15; R4/R1 = 1,37.
  5. Gebläserad (2) nach einem der Ansprüche 2 bis 4, wobei:
    - die Quotienten zwischen den Hilfsschaufelkurvenradien (r1, r2, r3) in etwa gleich den folgenden Werten sind: r2/r1 = 1,11; r3/r1 = 1,08; und
    - der erste Hilfsschaufelkurvenradius (r1) und der erste Hauptschaufelkurvenradius (R1) einen Quotienten aufweisen, der ungefähr gleich ist zu: r1/R1 = 1,25.
  6. Gebläserad (2) nach einem der vorhergehenden Ansprüche, wobei radiale Geraden (Toutpp), die tangential zu den Hauptschaufelbögen (PP) an den Auslassenden (33) der Hauptschaufeln (25) sind, mit radialen Graden (Routpp), die durch die Rotationsachse (A) und durch die Auslassenden (33) der Hauptschaufeln (25) verlaufen, Hauptschaufelaustrittswinkel (βoutpp) bilden, die zwischen 45°-55° liegen.
  7. Gebläserad (2) nach einem der vorhergehenden Ansprüche, wobei Geraden (Tinpp), die tangential zu den Hauptschaufelbögen (PP) an den Einlassenden (32) der Hauptschaufeln (25) sind, mit radialen Geraden (Rinpp), die durch die Rotationsachse (A) und durch die Einlassenden (32) der Hauptschaufeln (25) verlaufen, Hauptschaufeleintrittswinkel (βinpp) bilden, die zwischen 0°- 15° liegen.
  8. Gebläserad (2) nach den Ansprüchen 6 und 7, wobei die radialen Geraden (Routpp), die durch die Auslassenden (33) der Hauptschaufeln (25) verlaufen, und die radialen Geraden (Rinpp), die durch die Einlassenden (32) der Hauptschaufeln (25) verlaufen, Hauptschaufeleinschlusswinkel (⊝pp) bilden, die zwischen 15°-25° liegen.
  9. Gebläserad (2) nach dem vorhergehenden Anspruch, wobei:
    - die Hauptschaufelaustrittswinkel (βoutpp) Breiten von ungefähr gleich 50,4° aufweisen;
    - die Hauptschaufeleintrittswinkel (βinpp) Breiten von ungefähr gleich 12,9° aufweisen;
    - die Hauptschaufeleinschlusswinkel (⊝pp) Breiten von ungefähr gleich 22,8° aufweisen.
  10. Gebläserad (2) nach einem der Ansprüche 2 bis 9, wobei Geraden, die tangential zu den Hilfsschaufelbögen (PS) an den Auslassenden (35) der Hilfsschaufeln (29) sind, mit radialen Geraden, die durch die Rotationsachse (A) und durch die Auslassenden (35) der Hilfsschaufeln (29) verlaufen, Hilfsschaufelaustrittswinkel (βoutps) bilden, die zwischen 45°-55° liegen.
  11. Gebläserad (2) nach einem der Ansprüche 2 bis 10, wobei Geraden, die tangential zu den Hilfsschaufelbögen (PS) an den Einlassenden (34) der Hilfsschaufeln (29) sind, mit radialen Geraden, die durch die Rotationsachse (A) und durch die Einlassenden (34) der Hilfsschaufeln (29) verlaufen, Hilfsschaufeleintrittswinkel (βinps) bilden, die zwischen 25°-35° liegen.
  12. Gebläserad (2) nach den Ansprüchen 10 und 11, wobei die radialen Geraden, die durch die Auslassenden (35) der Hilfsschaufeln (29) verlaufen, und die radialen Geraden, die durch die Einlassenden (34) der Hilfsschaufeln (29) verlaufen, Hilfsschaufeleinschlusswinkel (⊝ps) bilden, die zwischen 15°-20° liegen.
  13. Gebläserad (2) nach dem vorhergehenden Anspruch, wobei:
    - die genannten Hilfsschaufelaustrittswinkel (βoutps) Breiten von ungefähr gleich 50,7° aufweisen;
    - die Hilfsschaufeleintrittswinkel (βinps) Breiten von ungefähr gleich 30,1° aufweisen;
    - die Hauptschaufeleinschlusswinkel (⊝ps) Breiten von ungefähr gleich 17,8° aufweisen.
  14. Gebläserad (2) nach einem der vorhergehenden Ansprüche, wobei die Auslassenden (33) der Hauptschaufeln (25) einen Gebläseradaußenumfang definieren, der einen Gebläseraddurchmesser (Dmax) aufweist, und die Einlassenden der Hauptschaufeln (25) einen Hauptschaufelinnenumfang definieren, der einen Hauptschaufelinnendurchmesser (dipp) aufweist, wobei der Gebläseraddurchmesser (Dmax) und der Hauptschaufelinnendurchmesser (dipp) einen Quotienten aufweisen, der in dem folgenden Bereich liegt: Dmax/dipp = 2 - 3,5.
  15. Gebläserad (2) nach dem vorhergehenden Anspruch, mit einer Gebläseradaxialhöhe (hext) an dem Gebläseradaußenumfang, wobei der Gebläseraddurchmesser (Dmax) und die Gebläseradaxialhöhe (hext) einen Quotienten in dem folgenden Bereich aufweisen: Dmax/hext = 6 - 9.
  16. Gebläserad (2) nach Anspruch 14 oder 15, wobei die Auslassenden (35) der Hilfsschaufeln (29) entlang des Gebläseradaußenumfangs angeordnet sind, und die Einlassenden (34) der Hilfsschaufeln (29) einen Hilfsschaufelinnenumfang definieren, der einen Hilfsschaufelinnendurchmesser (dips) aufweist, wobei der Gebläseraddurchmesser (Dmax) und der Hilfsschaufelinnendurchmesser (dips) einen Quotienten in dem folgenden Bereich aufweisen: Dmax/dips = 1,2-1,6.
  17. Gebläserad (2) nach dem vorhergehenden Anspruch, wobei:
    - der Gebläseraddurchmesser (Dmax) und die Gebläseradaxialhöhe (hext) einen Quotienten aufweisen von ungefähr gleich Dmax/hext = 7,37;
    - der Gebläseraddurchmesser (Dmax) und der Hauptschaufelinnendurchmesser (dipp) einen Quotienten aufweisen von ungefähr gleich Dmax/dipp = 2,78;
    - der Gebläseraddurchmesser (Dmax) und der Hilfsschaufelinnendurchmesser (dips) einen Quotienten aufweisen von ungefähr gleich Dmax/dips = 1,43.
  18. Gebläserad (2) nach einem der Ansprüche 14 bis 17, wobei der Gebläseraddurchmesser (Dmax) und der erste Hauptschaufelkurvenradius (R1) einen Quotienten in dem folgenden Bereich aufweisen: Dmax/R1 = 4 - 5.
  19. Gebläserad (2) nach dem vorhergehenden Anspruch, wobei der Gebläseraddurchmesser (Dmax) und der erste Hauptschaufelkurvenradius (R1) einen Quotienten aufweisen ungefähr gleich dem folgenden Wert: Dmax/R1 = 4,4.
  20. Gebläserad (2) nach einem der vorhergehenden Ansprüche, wobei die Hauptschaufeln (25) eine Hauptschaufeldicke (spp) aufweisen, die zwischen der ersten Hauptschaufeloberfläche (26) und der zweiten Hauptschaufeloberfläche (27) definiert ist, wobei der erste Hauptschaufelkurvenradius (R1) und die Hauptschaufeldicke (spp) einen Quotienten in dem folgenden Bereich aufweisen: R1/spp = 18-21.
  21. Gebläserad (2) nach dem vorhergehenden Anspruch, wobei der erste Hauptschaufelkurvenradius (R1) und die Hauptschaufeldicke (spp) einen Quotienten aufweisen ungefähr gleich zu R1/spp = 19,5.
  22. Gebläserad (2) nach Anspruch 20 oder 21, wobei die Hilfsschaufeln (29) eine Hilfsschaufeldicke (sps) aufweisen, die zwischen der ersten Hauptschaufeloberfläche (30) und der zweiten Hilfsschaufeloberfläche (31) definiert wird, wobei die Hauptschaufeldicke (spp) und die Hilfsschaufeldicke (sps) ungefähr konstant und im Wesentlichen gleich zueinander ausgebildet sind.
  23. Gebläserad (2) nach einem der vorhergehenden Ansprüche, wobei die Hauptschaufelkurvenradien in etwa die folgenden Werte aufweisen: R1 = 27,3 mm; R2 = 29 mm; R3 = 31,5 mm; R4 = 37,5 mm.
  24. Radialgebläse (1) mit einem Gehäuse (3), das einen Gebläseradraum (6) definiert, der geeignet ist, ein Gebläserad (2) nach einem der vorhergehenden Ansprüche aufzunehmen.
  25. Radialgebläse (1) nach dem vorhergehenden Anspruch, wenn dieser von Anspruch 15 abhängt, wobei der Gebläseradraum (6) des Gehäuses (3) eine Gehäuseaxialhöhe (Hall) aufweist, wobei die Gehäuseaxialhöhe (Hall) und die Gebläseradaxialhöhe (hext) einen Quotienten in dem folgenden Bereich aufweisen: Hall/hext = 1,2-1,3.
  26. Radialgebläse (1) nach dem vorhergehenden Anspruch, wobei die Gehäuseaxialhöhe (Hall) und die Gebläseradaxialhöhe (hext) einen Quotienten aufweisen ungefähr gleich zu: Hall/hext = 1,24.
  27. Radialgebläse (1) nach einem der Ansprüche 24 bis 26, wobei der Gebläseradraum (6) ein zu der Rotationsachse (A) des Gebläserads (2) transversales Transversalprofil besitzt, das einen Hauptabschnitt (45) aufweist, der als eine Vielzahl von aufeinanderfolgenden Kreisbögen ausgebildet ist.
  28. Radialgebläse (1) nach dem vorhergehenden Anspruch, wobei das Transversalprofil des Gebläseradraums (6) außerdem einen Auslassabschnitt (46) an einem Auslassstück (22) aufweist, das von dem Gehäuse (3) absteht, welches eine Auslassöffnung (21) für einen Luft- und/oder Gasaustritt aufweist, die in Strömungsverbindung mit dem Gebläseradraum (6) angeordnet ist.
  29. Radialgebläse (1) nach dem vorhergehenden Anspruch, wobei der Hauptabschnitt (45) einen ersten (CC1), einen zweiten (CC2), einen dritten (CC3) und einen vierten (CC4) Gehäusekreisbogen der Vielzahl von aufeinanderfolgenden Gehäusekreisbögen aufweist, die beginnend an dem Auslassabschnitt (46) mit einer Ausrichtung angeordnet sind, die entgegengesetzt zu der Rotationsrichtung des Gebläserads (2) ist, wobei die Gehäusekreisbögen (CC1, CC2, CC3, CC4) jeweils einen ersten (RC1), einen zweiten (RC2), einen dritten (RC3) und einen vierten (RC4) Gehäusekurvenradius aufweisen, wobei die Gehäusekurvenradien (RC1, RC2, RC3, RC4) Quotienten in den folgenden Bereichen aufweisen: RC ⁢ 1 / RC ⁢ 2 = 1 , 04 - 1 , 075 ; RC ⁢ 1 / RC ⁢ 3 = 1 , 075 - 1 , 15 ; RC ⁢ 1 / RC ⁢ 4 = 1 , 2 - 1 , 4.
    Figure imgb0002
  30. Radialgebläse (1) nach dem vorhergehenden Anspruch, wobei die Gehäusekurvenradien (RC1, RC2, RC3, RC4) die folgenden Quotienten aufweisen: RC1/RC2 = 1,06; RC1/RC3 = 1,09; RC1/RC4 = 1,29.
  31. Radialgebläse (1) nach Anspruch 29 oder 30, wobei der Gebläseraddurchmesser (Dmax) und der erste Gehäusekurvenradius (RC1) einen Quotienten in dem folgenden Bereich aufweisen: Dmax/RC1 = 1,5 - 1,8.
  32. Radialgebläse (1) nach dem vorhergehenden Anspruch, wobei der Quotient zwischen dem Gebläseraddurchmesser (Dmax) und dem ersten Gehäusekurvenradius (RC1) gleich ist zu in etwa 1,63.
  33. Radialgebläse (1) nach einem der Ansprüche 29 bis 32, wobei die Gehäusekurvenradien (RC1, RC2, RC3, RC4) in etwa die folgenden Werte aufweisen: RC1 = 74,1 mm; RC2 = 69,9 mm; RC3 = 68,2 mm; RC4 57,6 mm.
  34. Radialgebläse (1) nach einem der Ansprüche 28 bis 33, wobei der Auslassabschnitt (46) eine Breite (α) aufweist, die zwischen 60° und 80° liegt.
  35. Radialgebläse (1) nach einem der Ansprüche 28 bis 34, wobei das Gehäuse (3) außerdem eine Förderzunge (47) aufweist, die in dem Gebläseradraum (6) an dem Auslassabschnitt (46) angeordnet ist, wobei die Förderzunge (47) sich entlang einer Zungenachse (L) erstreckt, die einen im Wesentlichen geradlinigen Abschnitt aufweist und ein graduell ansteigendes Teilstück in Richtung der Auslassöffnung (21) entlang der Zungenachse (L) besitzt.
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