EP3571416B1 - Gedecktes radialgebläserad mit einer periodisch und asymmetrisch geformten scheibe - Google Patents
Gedecktes radialgebläserad mit einer periodisch und asymmetrisch geformten scheibe Download PDFInfo
- Publication number
- EP3571416B1 EP3571416B1 EP18762797.1A EP18762797A EP3571416B1 EP 3571416 B1 EP3571416 B1 EP 3571416B1 EP 18762797 A EP18762797 A EP 18762797A EP 3571416 B1 EP3571416 B1 EP 3571416B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- fan wheel
- blade
- radial
- axial width
- blades
- 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
Links
- 238000010586 diagram Methods 0.000 description 4
- 238000000926 separation method Methods 0.000 description 3
- 230000008092 positive effect Effects 0.000 description 2
- 230000007423 decrease Effects 0.000 description 1
- 238000011161 development Methods 0.000 description 1
- 230000018109 developmental process Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000002349 favourable effect Effects 0.000 description 1
- 230000002093 peripheral effect Effects 0.000 description 1
- 239000007787 solid Substances 0.000 description 1
Images
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
- F04D29/26—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
- F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
- F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps
- F04D29/666—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps by means of rotor construction or layout, e.g. unequal distribution of blades or vanes
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
- F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps
- F04D29/667—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps by influencing the flow pattern, e.g. suppression of turbulence
-
- 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
- F04D29/02—Selection of particular materials
- F04D29/023—Selection of particular materials 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
- F04D29/40—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
- 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
Definitions
- the invention relates to a radial fan wheel with a plurality of fan wheel blades arranged in a blade ring and at least one disc which covers the fan wheel blades axially at least in sections on the front side.
- Radial fan wheels are known from the prior art in various designs and are used in a variety of blowers with different purposes. It is also known that flow separations should be avoided as much as possible, as these reduce the efficiency of the blowers or fans and lead to increased noise. Typically, the suction side of the impeller blades tends to cause flow separation during operation due to boundary layer overloading, while the flow is on the pressure side of the impeller blades.
- the invention is therefore based on the object of providing a fan wheel which leads to increased efficiency and improved noise behavior in radial blowers.
- a radial impeller according to claim 1 is proposed.
- the radial fan wheel has a plurality of fan wheel blades arranged in a blade ring and at least one disk which covers the fan wheel blades axially on the front side at least in sections, with two adjacent fan wheel blades each forming a blade channel between them, the flow cross section of which is limited axially by the disk.
- the axial width of the blade channel increases at least along an outer circumference of the radial fan wheel, starting from a suction side of a fan wheel blade delimiting the blade channel towards a pressure side of the adjacent fan wheel blade delimiting the blade channel, up to a maximum.
- the maximum lies on a radial section of the fan wheel, which lies between 65 - 80% of the distance between the suction side of the fan wheel blade delimiting the blade channel and the pressure side of the adjacent fan wheel blade delimiting the blade channel, so that the disk, viewed in the circumferential direction, is asymmetrical between two adjacent fan wheel blades has shape.
- the asymmetrical design of the disk of the radial fan wheel according to the invention leads to a narrowing of the blade channel in the area of the suction side of the fan wheel blade and to an enlargement of the blade channel or its flow cross-sectional area in the area of the pressure side of the fan wheel blade. This stabilizes the flow in the area of the suction side and prevents or minimizes flow separation.
- the increase in the flow cross-section takes place in particular without abruptly changing the course of the flow cross-section and therefore advantageously through a constant course of the disk in the circumferential direction.
- the disk between all adjacent fan wheel blades is of identical shape, so that the flow channels running between the fan wheel blades are also each of the same shape.
- an embodiment of the radial impeller is favorable in which the impeller blades have a constant axial width, in particular at the outer radius of the radial impeller.
- the entire fan wheel blades of the blade ring are designed to have identical shapes in an advantageous solution.
- b x B.S + BE ⁇ BE P ⁇ X / P 2 with X ⁇ P
- b x B.S + BE ⁇ BE X ⁇ P / 1 ⁇ P 2 with X > P , as well as 0 ⁇ P ⁇ 1 , certainly.
- BS corresponds to an axial width of the blade channel on the impeller blade, BE to the expansion of the axial width of the blade channel up to the maximum, P to a position of the maximum of the axial width of the blade channel starting from the suction side of the impeller blade delimiting the blade channel and X to a circumferential direction of a developed cut along the Disc contour, ie a course along the outer contour of the radial fan wheel.
- the axial width of the respective blade channel increases to the maximum at position P and then decreases again.
- the formulas express the course of the axial width of the blade channel in the circumferential direction between two adjacent impeller blades. On the adjacent impeller blades, the value of the axial width corresponds to BS. In the area in between, the axial width of the blade channel increases by the extension BE with the off-center maximum of the axial width B.
- an advantageous embodiment provides that the disk is formed by the suction-side cover disk.
- the invention is not limited to this, so that the disk can also be realized by the base disk, which usually also forms at least parts of the hub of the radial fan wheel.
- the increase in the axial width of the flow cross section of the flow channel is formed by both the base and the cover plate with a correspondingly asymmetrical contour on both sides is.
- the fan wheel blades are preferably curved in the circumferential direction and are flush with the outer edge of the base disk and/or cover disk.
- FIGS. 1 and 2 show an exemplary embodiment of a radial fan wheel 1 with a plurality of backwardly curved blades arranged in a blade ring Impeller blades 4, the lower axial end faces of which are completely covered by the bottom disk 3, which extends parallel to the axial plane running perpendicular to the axis of rotation of the radial impeller 1.
- the fan wheel blades 4 are partially covered with the suction-side cover plate 2, the fan wheel blades 4 being exposed in the area of the suction opening 7 of the radial fan wheel 1 and extending with an arcuate radial end edge in the direction of the base plate 3.
- the suction opening 7 is formed by the circular peripheral edge 9.
- Two adjacent fan blades 4 each form a blade channel 5 between them, the flow cross sections of which are determined and limited by the fan blades 4, the flat base disk 3 and the cover disk 2.
- all impeller blades 4 are identical and have a constant axial width.
- All flow channels 5 also have the identical shape, since the cover plate 2 between all adjacent fan wheel blades 4 is also designed to have the same shape.
- the axial width B of the respective blade channel 5 is not constant over the extent in the circumferential direction of the radial fan wheel 1, but is adjusted via the shape of the cover disk, so that it extends from the suction side S of the fan wheel blade 4 in the direction of the pressure side D of the adjacent fan wheel blade 4 an axial width of the fan wheel blade BS increases to the maximum M and then reduces back to the size of the axial width BS of the adjacent fan wheel blade 4.
- the course of the cover plate 2 is continuous.
- the maximum is off-center and on a radial section of the radial fan wheel 1, which in the embodiment shown is at 75% of the distance between the suction side S of the fan wheel blade 4 and the pressure side D of the adjacent fan wheel blade 4, measured at the outer radius of the radial fan wheel 1, so that the Cover plate 2 seen in the circumferential direction between two adjacent ones Fan wheel blades 4 have an asymmetrical shape.
- the asymmetrical shape is determined in particular on the outer radius of the radial fan wheel 1, but also runs radially inwards over a certain length, so that a three-dimensional axial width increase is present in the radial outer area of the pressure side D of the individual fan wheel blades 4.
- the asymmetrical shape of the cover plate 2 continuously changes into a symmetrical shape in the direction pointing radially inwards towards the suction opening 7, with the collar 8 adjacent to the suction opening already being designed as a ring.
- FIG 3 is a diagram of the course of the axial width B of the blade channel 5 along the circumferential direction X of the radial fan wheel 1 Fig. 1 at its outer radius and therefore the ratio of the flow cross-sectional area of one of the flow channels 5 at the flow channel outlet.
- the center Z of the blade channel 5 between two adjacent impeller blades 4 is represented by the dot-dash line, with the suction side S lying to the left of the center Z and the pressure side of the impeller blades 4 to the right of the center Z.
- the mean axial width MB is shown as a dashed line.
- the maximum M of the axial width B is entered as a dotted line at 75% of the distance between the suction side S of the impeller blade 4 and the pressure side D of the adjacent impeller blade 4.
- FIG 4 is a diagram with characteristic curves measured with an identical test setup for the pressure curve psf [Pa] and the efficiency nse [%] at different volume flows qv [m 3 /h] of the radial fan wheel 1 Fig. 1 and the identical radial fan wheel 100 only with a flat cover plate 200 Figure 5 shown, with the solid characteristics showing the radial fan wheel 1 according to Figure 1 with the cover plate 2 and the fine-dotted characteristic curves each correspond to the radial fan wheel 100 Figure 5 mark.
- the advantageous effect with increased peak efficiency starts with a volume flow of approx. 150 m 3 /h and upwards.
- the superior pressure curve starts at approx. 225 m 3 /h.
- the reduction in noise generation is at least 5% in the range from 225 m 3 /h.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102017120537.3A DE102017120537A1 (de) | 2017-09-06 | 2017-09-06 | Radialgebläserad mit asymmetrischer Scheibe |
PCT/EP2018/072693 WO2019048241A1 (de) | 2017-09-06 | 2018-08-22 | Gedecktes radialgebläserad mit einer periodisch und asymmetrisch geformten scheibe |
Publications (2)
Publication Number | Publication Date |
---|---|
EP3571416A1 EP3571416A1 (de) | 2019-11-27 |
EP3571416B1 true EP3571416B1 (de) | 2023-10-04 |
Family
ID=63222494
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP18762797.1A Active EP3571416B1 (de) | 2017-09-06 | 2018-08-22 | Gedecktes radialgebläserad mit einer periodisch und asymmetrisch geformten scheibe |
Country Status (5)
Country | Link |
---|---|
US (1) | US11143197B2 (zh) |
EP (1) | EP3571416B1 (zh) |
CN (1) | CN207777266U (zh) |
DE (1) | DE102017120537A1 (zh) |
WO (1) | WO2019048241A1 (zh) |
Families Citing this family (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
USD949315S1 (en) * | 2016-06-24 | 2022-04-19 | Ebm-Papst Mulfingen Gmbh & Co. Kg | Vane damper with trailing edge |
DE102020114389A1 (de) * | 2020-05-28 | 2021-12-02 | Ebm-Papst Mulfingen Gmbh & Co. Kg | Gebläserad mit ener nahtlosen Anbindung der Laufradschaufeln an einen Scheibenkörper |
DE102022113706A1 (de) | 2022-05-31 | 2023-11-30 | Ebm-Papst Mulfingen Gmbh & Co. Kg | Kühlrad zur aktiven Kühlung eines Stators eines Elektromotors |
Family Cites Families (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2008223741A (ja) * | 2007-03-16 | 2008-09-25 | Daikin Ind Ltd | 遠心送風機 |
JP5634782B2 (ja) * | 2009-08-11 | 2014-12-03 | 山洋電気株式会社 | 遠心ファン |
JP4902718B2 (ja) | 2009-10-07 | 2012-03-21 | 三菱電機株式会社 | 遠心送風機および電気掃除機 |
DE202010018509U1 (de) * | 2010-02-26 | 2017-03-15 | Ebm-Papst Mulfingen Gmbh & Co. Kg | Radial- oder Diagonal-Ventilatorrad |
JP5783305B2 (ja) | 2013-09-18 | 2015-09-24 | ダイキン工業株式会社 | ギヤ流体装置 |
KR101720491B1 (ko) * | 2015-01-22 | 2017-03-28 | 엘지전자 주식회사 | 원심팬 |
KR102257480B1 (ko) * | 2015-03-24 | 2021-05-31 | 삼성전자주식회사 | 원심팬 |
-
2017
- 2017-09-06 DE DE102017120537.3A patent/DE102017120537A1/de active Pending
-
2018
- 2018-01-05 CN CN201820017251.4U patent/CN207777266U/zh active Active
- 2018-08-22 US US16/607,321 patent/US11143197B2/en active Active
- 2018-08-22 WO PCT/EP2018/072693 patent/WO2019048241A1/de unknown
- 2018-08-22 EP EP18762797.1A patent/EP3571416B1/de active Active
Also Published As
Publication number | Publication date |
---|---|
DE102017120537A1 (de) | 2019-03-07 |
CN207777266U (zh) | 2018-08-28 |
US11143197B2 (en) | 2021-10-12 |
WO2019048241A1 (de) | 2019-03-14 |
EP3571416A1 (de) | 2019-11-27 |
US20200080565A1 (en) | 2020-03-12 |
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