EP3607210B1 - Soufflante radiale - Google Patents

Soufflante radiale Download PDF

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Publication number
EP3607210B1
EP3607210B1 EP18714239.3A EP18714239A EP3607210B1 EP 3607210 B1 EP3607210 B1 EP 3607210B1 EP 18714239 A EP18714239 A EP 18714239A EP 3607210 B1 EP3607210 B1 EP 3607210B1
Authority
EP
European Patent Office
Prior art keywords
spacing
cross
end wall
sectional area
air
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.)
Active
Application number
EP18714239.3A
Other languages
German (de)
English (en)
Other versions
EP3607210A1 (fr
Inventor
Peter Ragg
Christian Moosmann
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.)
Ebm Papst St Georgen GmbH and Co KG
Original Assignee
Ebm Papst St Georgen 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 Ebm Papst St Georgen GmbH and Co KG filed Critical Ebm Papst St Georgen GmbH and Co KG
Publication of EP3607210A1 publication Critical patent/EP3607210A1/fr
Application granted granted Critical
Publication of EP3607210B1 publication Critical patent/EP3607210B1/fr
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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
    • F04D29/40—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
    • F04D29/26—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
    • F04D29/08—Sealings
    • F04D29/16—Sealings between pressure and suction sides
    • F04D29/161—Sealings between pressure and suction sides especially adapted for elastic fluid pumps
    • F04D29/162—Sealings between pressure and suction sides especially adapted for elastic fluid pumps of a centrifugal flow wheel
    • 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
    • F04D29/4206—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps
    • F04D29/4226—Fan casings
    • 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
    • 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
    • F04D29/4206—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps
    • F04D29/4213—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps suction ports
    • 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
    • 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
    • F05D2250/712—Shape curved concave

Definitions

  • the present invention relates to a radial fan with a fan wheel which can be rotated about an axis and which comprises a base plate and air blades protruding from the base plate.
  • a cover is placed on the edges of the air blades facing away from the base plate, which cover rotates together with the base plate and the air blades and together with the base plate delimits a flow channel through which air is pumped by the rotation of the fan wheel.
  • Such an air scoop is comparatively expensive to produce, since it has to be assembled from several parts, and it has a rather high moment of inertia.
  • the edges of the air vanes directly face an end wall that is not connected to and does not rotate with the fan wheel.
  • Such an open fan wheel is easier and cheaper to manufacture and has a lower moment of inertia than the fan wheel with a cover.
  • the object of the invention is to create a radial fan that is simple and inexpensive to manufacture and yet is highly efficient.
  • the difference between the fourth distance and the second distance should be less than the difference between the third distance and the fourth distance.
  • the former difference can be zero, ie the minimum can with the downstream edges of the air vanes coincide.
  • the difference between the cross-sectional areas does not have to be large, in order to observe a clear effect, it is sufficient if the cross-sectional area at the fourth distance is 4% smaller than at the third distance. A difference of 10% or more can lead to a disturbing impairment of the volumetric flow.
  • the difference between the third distance and the fifth distance should also be at least a quarter of the difference between the first and the second distance.
  • the cross-sectional area at the fifth distance may be smaller than that at the fourth distance; it can deviate from that of the third distance by more than 8%.
  • the radius of curvature of the end wall in the radial section between the first and second distances is preferably nowhere less than a quarter of the first distance.
  • the maximum of the cross-sectional area is formed by a concave surface area of the end wall in the radial section at the third distance from the axis.
  • the minimum radius of curvature of this concave surface area is greater than that of the entire end wall, it is selected according to the invention at least equal to the first distance.
  • the air vanes can each have a projection which engages in the concave surface region at the third distance from the axis.
  • the cross-sectional area is calculated as the product of a distance from the axis and the axial distance between the end wall and the base plate measured at this distance.
  • the fan wheel can be manufactured inexpensively by molding in one piece, in particular by injection molding.
  • the end wall can be part of a housing that forms a wheel chamber enclosing the fan wheel.
  • the wheel chamber can also include a blown air channel that extends around the fan wheel and in which the air conveyed by the fan wheel can accumulate.
  • An overpressure in the blast air duct can be used to cool an engine by a cooling air duct emanating from the blast air duct.
  • the air used to cool the motor is expediently fed back into the wheel chamber.
  • the opening of the cooling air duct into the wheel chamber can be arranged opposite the base plate of the impeller.
  • FIG. 1 shows a radial fan according to the invention in section along an axis of rotation 1 of its fan wheel 2.
  • shaft 3 rotor 4 and stator 5 of an electric motor 6 as well as a printed circuit board 7 carrying an inverter for powering the motor 6, enclosed in an inner casing 8.
  • the inner casing 8 comprises a cup 9 which houses the motor 6 and the circuit board 7, and a lid 10 which closes the cup 9 and through the central opening of which the shaft 3 protrudes.
  • An outer housing 11 comprises a base plate 12, an outer wall 13, an annular intermediate wall 14 and an end wall 15.
  • the base plate 12 is connected to the outer wall 13 via an elastic buffer ring 16 to form a second, outer cup, which forms the inner cup 9 of a cooling air duct 17 extending annularly around the inner cup 9 and the motor 6 .
  • the outer wall 13 has two shoulders 18, 19 on its inside, on which its diameter decreases towards the base plate 12 in each case.
  • the intermediate wall 14 is pushed into the cavity surrounded by the outer wall 13 in such a way that an edge of the intermediate wall 14 rests on the shoulder 18 near the ground. In this position, the outer wall 13 and the intermediate wall 14 together delimit a blast air channel 20, the bottom of which forms the shoulder 19.
  • the blast air duct 20 extends around the shaft 1 with a gradually increasing cross section and, after one revolution around the axis 1, merges into a tangentially branching outlet duct 21.
  • a passage 22 is cut out at the bottom of the blown air duct 20 between the outer wall 13 and the intermediate wall 14 , which passage connects the blown air duct 20 to the cooling air duct 17 .
  • the cover 10 of the inner housing 8 engages in a central opening of the intermediate wall 14 .
  • a further elastic buffer ring 23 extends between the cover 10 and the intermediate wall 14.
  • the inner housing 8 is vibration-damped by the buffer rings 16, 23 relative to the outer wall 13, so that vibrations of the motor 6 are only passed on to the environment to a small extent as structure-borne noise .
  • the end wall 15 is attached to the outer wall 13 with the aid of claws 24 (see Fig. 2 , 3 ) snapped into place, encompassing the projections on the outer wall 13 .
  • the wheel chamber 25 accommodates the fan wheel 2 which is attached to one end of the shaft 3. Its rotation causes air to flow through a central inlet opening in a manner known per se 26 of the end wall 15 is sucked into the wheel chamber 25, driven radially outwards into the blown air channel 20 and discharged back to the outside via its outlet channel 21.
  • the intermediate wall 14 has one or more openings 27 adjacent to the end of the blower air duct 20 facing away from the outlet duct 21 and communicating with the cooling air duct 17. These openings 27 are in the representation of 2 covered by the fan wheel 2 and therefore shown with dashed lines.
  • the rotation of the fan wheel 2 generates a higher pressure in front of the passage 22 than at the openings 27, so that air enters the cooling air duct 17 via the passage 22, absorbs waste heat from the engine 6 there and then returns to the wheel chamber 25 via the openings 27.
  • a radial wall 28 between the cup 9 and the outer wall 13 divides the cooling air duct 17 and forces the sucked-in air to encircle the cup 9 almost completely on the way from the passage 22 to the openings 27 .
  • the fan wheel 2 comprises a base plate 29 which, together with the end wall 15, delimits a flow channel 30 in which the air is driven radially outwards by the rotation of the fan wheel 2, and a multiplicity of air blades 31, which face from a surface facing the end wall 15 of the base plate 29 protrude into the flow channel 30 .
  • the air vanes 31 are in the form of ribs, each extending substantially radially from a radially inner upstream edge 32 to a downstream edge 33 and having an elongated crest edge 34 a short distance opposite the end wall 15 .
  • the upstream edges 32 and downstream edges 33 of the air vanes 31 lie on circles about the axis 1 with radii r1, r2.
  • the surface of the base plate 29 has approximately the shape of a hyperboloid of revolution centered on the axis 1 in an annular region 35 between the two circles.
  • the opening angle of such a cone does not change significantly between r1 and r2 and it is not a question of absolute cross-sectional areas but only of their ratio to one another, a further simplification can be made and the cone surface can be replaced by a cylinder surface, i.e. as a dimension for the cross-sectional area, the product of the distance between the base plate 29 and the end wall 15 measured in the direction of the axis 1 and the distance r of the location of the measurement from the axis 1 is taken.
  • this contour 36 detaches itself tangentially from the real surface of the end wall 15 at a point 37 in order to initially run through the material of the end wall 15 up to a point 38; from the point 38 it runs through the flow channel 30 until it hits the surface of the end wall 15 again at a point 39 .
  • the cross-sectional area of the flow channel 30 is smaller between points 37 and 38 and larger between points 38, 39 than at points 37, 38, 39.
  • a diagram in the lower right corner of 3 Figure 12 quantitatively shows the cross-sectional area A of the flow channel 30 as a function of the distance r from the axis 1, the cross-sectional area at the distance r2 of the downstream edges 33 being arbitrarily set equal to 1.
  • the area A first decreases to a minimum at r5, in order to then reach a maximum at r3 and from there to strive for a minimum again, whose distance r4 here corresponds to the distance r2 of the downstream edges 33 matches.
  • the distance r4-r5 between the two minima here corresponds to about two-thirds of the distance r2-r1 between the edges 33, 32.
  • the decrease in cross-section from r3 to r4 is considerably slower than the increase from r5 to r3, so that although the difference in Cross-sectional areas between r5 and r3 is greater than between r3 and r4, the distance r3-r5 is significantly smaller than r4-r3.
  • the end wall 24 has a concavely curved surface area 41 between surface areas 40, 42 that are convexly curved in radial section.
  • the radius of curvature of the entire end wall 24 should not be too small to an abrupt deflection of the to avoid air and vortex formation.
  • the smallest value R1 of the radius of curvature is reached here at distance r5, R1 > 0.5 r1 applies.
  • the minimum radius of curvature R2 of the concave portion 41 is even larger, for which R2 > r1.
  • Projections 43 of the air vanes 31 face the surface area 41 such that the width of a gap between the apex edges 34 of the air vanes 31 and the end wall 24 remains substantially constant over the entire length of the apex edges 34 .

Landscapes

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

Claims (8)

  1. Ventilateur radial, comprenant une roue de ventilateur (2) pouvant tourner autour d'un axe (1) et qui comprend une plaque de base (29) et des aubes (31) faisant saillie à partir de la plaque de base (29), les aubes (31) présentant respectivement un bord amont (32) à une première distance (r1) de l'axe (1) et un bord aval (33) à une deuxième distance (r2) de l'axe (1), et comprenant une paroi frontale (15) qui délimite conjointement avec la plaque de base (29) un conduit d'écoulement (30) dans lequel les aubes (31) viennent en prise, dans lequel la superficie de la section (A) du conduit d'écoulement (30) passe par un maximum entre le bord amont (32) et le bord aval (33) à une troisième distance (r3) de l'axe (1), et la différence entre une quatrième distance (r4) et une cinquième distance (r5) auxquelles la superficie de la section (A) adopte respectivement des minima immédiatement voisins du maximum est égale à au moins la moitié de la différence (r2-r1) entre la première et la deuxième distance, la superficie de la section (A) étant calculée comme le produit d'une distance (r) de l'axe (1) et l'écartement axial, mesuré à cette distance (r), entre la paroi frontale (15) et la plaque de base (29), et la paroi frontale (15) présentant à la troisième distance (r3) de l'axe une zone de surface (41) concave en coupe radiale,
    caractérisé en ce que la zone de surface concave (41) présente en coupe radiale un rayon de courbure (R2) qui correspond au moins à la première distance (r1).
  2. Ventilateur radial selon la revendication 1, caractérisé en ce que la quatrième distance (r4) est supérieure à la deuxième distance (r2), et la différence (r4-r2) entre la quatrième distance et la deuxième distance est inférieure à la différence (r4-r3) entre la troisième distance et la quatrième distance.
  3. Ventilateur radial selon la revendication 2, caractérisé en ce que la superficie de la section (A) à la quatrième distance (r4) est inférieure d'au moins 4 % qu'à la troisième distance (r3).
  4. Ventilateur radial selon l'une quelconque des revendications précédentes, caractérisé en ce que la cinquième distance (r5) est inférieure à la troisième distance (r3), et la différence (r3-r5) entre la troisième distance et la cinquième distance est au moins un quart de la différence entre la première et la deuxième distance (r2-r1).
  5. Ventilateur radial selon la revendication 4, caractérisé en ce que la superficie de la section (A) à la cinquième distance (r5) est inférieure qu'à la quatrième distance (r4).
  6. Ventilateur radial selon la revendication 4 ou 5, caractérisé en ce que la superficie de la section (A) à la cinquième distance (r5) est inférieure d'au moins 8 % à la superficie de la section (A) à la troisième distance (r3).
  7. Ventilateur radial selon l'une quelconque des revendications précédentes, caractérisé en ce qu'un rayon de courbure (R1) de la paroi frontale (15) en coupe radiale entre la première et la deuxième distance (r1, r2) n'est pas inférieur à un quart de la première distance (r1).
  8. Ventilateur radial selon l'une quelconque des revendications précédentes, caractérisé en ce que les aubes (31) à la troisième distance (r3) de l'axe (1) présentent respectivement une saillie (43) opposée à la zone de surface concave (41).
EP18714239.3A 2017-04-07 2018-03-28 Soufflante radiale Active EP3607210B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102017003431.1A DE102017003431A1 (de) 2017-04-07 2017-04-07 Radiallüfter
PCT/EP2018/057944 WO2018184946A1 (fr) 2017-04-07 2018-03-28 Ventilateur radial

Publications (2)

Publication Number Publication Date
EP3607210A1 EP3607210A1 (fr) 2020-02-12
EP3607210B1 true EP3607210B1 (fr) 2022-05-04

Family

ID=61827745

Family Applications (1)

Application Number Title Priority Date Filing Date
EP18714239.3A Active EP3607210B1 (fr) 2017-04-07 2018-03-28 Soufflante radiale

Country Status (9)

Country Link
US (1) US11105335B2 (fr)
EP (1) EP3607210B1 (fr)
CN (1) CN210738914U (fr)
DE (2) DE102017003431A1 (fr)
ES (1) ES2919432T3 (fr)
HU (1) HUE058983T2 (fr)
PL (1) PL3607210T3 (fr)
PT (1) PT3607210T (fr)
WO (1) WO2018184946A1 (fr)

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102016001484A1 (de) * 2016-02-11 2017-08-17 Ebm-Papst St. Georgen Gmbh & Co. Kg Lüftereinheit

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS595896A (ja) * 1982-07-01 1984-01-12 Matsushita Electric Ind Co Ltd 送風機
JPS5928096A (ja) * 1982-08-06 1984-02-14 Matsushita Electric Ind Co Ltd 送風機
FR2832770B1 (fr) * 2001-11-27 2004-01-02 Mallinckrodt Dev France Turbine centrifuge pour dispositifs d'assistance respiratoire
DE102006057086B8 (de) 2006-12-04 2009-01-29 Minebea Co., Ltd. Gebläse für ein Gasverbrennungssystem
JP6155544B2 (ja) * 2012-03-12 2017-07-05 日本電産株式会社 遠心ファン

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102016001484A1 (de) * 2016-02-11 2017-08-17 Ebm-Papst St. Georgen Gmbh & Co. Kg Lüftereinheit

Also Published As

Publication number Publication date
HUE058983T2 (hu) 2022-09-28
EP3607210A1 (fr) 2020-02-12
DE212018000127U1 (de) 2019-08-16
DE102017003431A1 (de) 2018-10-11
CN210738914U (zh) 2020-06-12
WO2018184946A1 (fr) 2018-10-11
US11105335B2 (en) 2021-08-31
ES2919432T3 (es) 2022-07-26
PT3607210T (pt) 2022-08-16
PL3607210T3 (pl) 2022-07-18
US20190376525A1 (en) 2019-12-12

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