EP1961969A2 - Roue de ventilateur radiale - Google Patents

Roue de ventilateur radiale Download PDF

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Publication number
EP1961969A2
EP1961969A2 EP08151624A EP08151624A EP1961969A2 EP 1961969 A2 EP1961969 A2 EP 1961969A2 EP 08151624 A EP08151624 A EP 08151624A EP 08151624 A EP08151624 A EP 08151624A EP 1961969 A2 EP1961969 A2 EP 1961969A2
Authority
EP
European Patent Office
Prior art keywords
fan
blades
flow
fan wheel
support member
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Withdrawn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
EP08151624A
Other languages
German (de)
English (en)
Other versions
EP1961969A3 (fr
Inventor
Josip Pavetic
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.)
Individual
Original Assignee
Individual
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
Priority claimed from EP07003875A external-priority patent/EP1961966A1/fr
Application filed by Individual filed Critical Individual
Priority to EP08151624A priority Critical patent/EP1961969A3/fr
Publication of EP1961969A2 publication Critical patent/EP1961969A2/fr
Publication of EP1961969A3 publication Critical patent/EP1961969A3/fr
Withdrawn legal-status Critical Current

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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
    • F04D29/289—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps having provision against erosion or for dust-separation

Definitions

  • the invention relates to an axial impinged radial impeller for conveying a particle-laden fluid, with a driven support member which extends substantially perpendicular to a rotation axis and carries a blade arrangement with a plurality of annularly spaced circumferentially spaced impeller blades, each one radially have inside leading edge and a radially outer outlet edge and between which radially outwardly directed flow channels are fixed, whereby an axial inlet flow is radially deflected outward.
  • Such a radial fan is, for example, from the documents EP 0 615 069 A1 .
  • the invention has for its object to provide such a radial impeller such that it is particularly suitable for the purification of fluid in which particularly coarse particles, such as large water or other liquid droplets or coarse dust particles are included.
  • the radial impeller is provided at the point where the flow velocity of the fluid is relatively small, with additional blades, which can be used in this way particularly effective, primarily heavy particles in the fluid, which does not divert the flow due to their inertia can join, can be transported radially outward, on that side of the radial impeller on which is usually the separation ring gap.
  • additional blades affect the flow resistance and thus the efficiency of the radial impeller only slightly, since they are arranged at an already low flowed through point.
  • the force component acting on the particles to be separated and directed onto the carrier part can in principle be produced in various ways, for example by flow forces induced by the additional blades.
  • a particularly effective particle separation for heavy particles results according to the invention by the pulse introduced by the additional blades onto the particles, which has a component which is directed towards the carrier part. It has been shown in experiments that with these measures in coarse dust-laden fluids deposition efficiencies can be achieved, which are about a factor of 2 over the conventional blowers.
  • the main blades are also given a function which transmits the particles with a specific, directed impulse.
  • the employed in this way fan blades affect the flow resistance and thus the efficiency of the radial impeller also only slightly.
  • auxiliary webs can be omitted on the Lüfterradschaufeln, whereby the flow resistance in the radial impeller can be kept very small.
  • a particularly advantageous development of the radial impeller which is particularly suitable for cleaning fluid with a mix of particles of different sizes, is the subject of claim 3.
  • the heavier particles are still in the center of the radial impeller of the Additional blades transported to the separation annular gap, while the smaller in weight particles are pushed over the strip-like projections on the working or pressure sides of the fan blades at the radial flow gradually towards the support member and thus to the deposition annular gap.
  • this development is particularly effective for the purification of fluid, which is loaded simultaneously with liquid and solid particles. This results in the further additional advantage that not only the fan blades as a whole, but also the strip-like projections get a longer service life, since the predominantly responsible for the wear particles are separated from the additional blades.
  • each strip can be individually designed so that it effectively detects and deposits the particulate fraction present specifically at this axial point of the fan.
  • the auxiliary blades are circumferentially offset to the fan blades, preferably such that the heavy particles captured by the radially outer portions of the auxiliary blades do not strike the front edge of the fan blades in their radially outward movement.
  • This effect can also be achieved in a simple manner in that the fan blades and the additional blades have an overlap or overlap in the radial direction.
  • the radial impeller receives a higher stability, so that the hub the support member can be made shallower and more design latitude in the construction of the fan blades remains.
  • the additional blades can be formed in the center with a greater axial extension, whereby their effectiveness is increased.
  • the reference numeral 10 generally indicates an axially impinged radial impeller, which is used for conveying a fluid or fluid, in particular a fluid laden with solid or liquid particles.
  • the impeller 10 should be able to largely separate the particles, such as dust particles, water particles, snowflakes, fat particles and the like., When Durschströmen the fan.
  • the fan 10 has a rotation axis 12, which - as best of the FIG. 7 recognizes - when mounting in a fan 14, for example, vertically aligned.
  • a designated 16 hub rotatably seated on a drive shaft, not shown, with the axis 12 and it carries a blade support member 18, which extends substantially perpendicular to the axis of rotation 12.
  • the support member 18 in turn carries a blade assembly with a plurality of annularly spaced circumferentially spaced and generally identically formed fan blades 20, which are aligned parallel to the axis of rotation 12, but to an axis 12 containing the axis of rotation 12, such as the plane of the FIG. 7 , Are set to produce when turning the fan 10 with the direction of rotation V a radially outward flow.
  • the fan blades 20 are straight, resulting from the FIG. 1 results.
  • the blade shape can be modified as desired in order to improve the flow-mechanical efficiency of the fan and / or the particle separation to be described later.
  • the Lüfterradschaufeln 20 each have a radially inner leading edge 24 and a radially outer trailing edge 26. Between the fan blades 20 are substantially radially outwardly directed flow channels 28 defined, so that an axial inlet flow - indicated by the arrow SE - with rotating fan 10th radially outward into an outlet flow SA with radial and directed in the circumferential direction velocity component is deflected.
  • FIGS. 1 to 3 show the leading edges 24 and flow outlet edges 26 each have a pitch circle 24a or 26a assigned.
  • the flow entry edges 24 extend from a portion of the support member 18 proximate to the hub 16 and extend axially therefrom to a blade edge 29 substantially parallel to the support member 18 (see FIGS FIG. 3 and 7 ).
  • the fan blades 20 carry an annular disc 21st
  • the shape of the Lüfterradschaufeln 20 may vary depending on the fan design - within wide limits.
  • the construction of the fan wheel becomes stiffer, so that it is sufficient to attach the fan blades to the support member 18, e.g. to weld.
  • the leading edge 24 of the fan blades can then be arranged substantially parallel to the axis of rotation.
  • the fan 10 is installed in the housing 14 of the Radialgebläsesso that it comes to rest below an axial inlet funnel 30, which is aligned with the axis of rotation 12 of the fan 10. Radially from the outside, the impeller 10 is enclosed by an annular channel 32, which has an outlet 34 for the fluid largely freed from the particles.
  • the annular channel 32 has a bottom surface 36, which closely conforms to the radially outer blade edges 26.
  • the fan wheel 10 may also be provided with a bottom-side recess (not shown) into which the bottom surface 36 of the annular channel 32 engages with a fit.
  • the bottom surface 36 of the annular channel 32 to a support member 14 nearest edge 38 of the fan blades 20 axially spaced by a predetermined gap MS.
  • the bottom surface 36 of the annular channel 32 defines a radial or annular gap 40 for discharging particles deposited from the fluid, such as dust, water, oil or grease particles.
  • the annular gap 40 is surrounded by a further annular chamber 42 for collecting and discharging the particles separated from the fluid.
  • the fluid flowing in at 30 during the flow through the radial blower can be effectively cleaned of primarily coarse or heavy solid or liquid particles, are on the support member or (in the variant according to FIG. 7 attached to the hub 16) radially within the fan blades 20 additional axially projecting from the support member 18 additional blades 44. These are set in the direction of rotation V of the fan 10 such that in the fluid to be conveyed particles under the action of the impulse force, the centrifugal force and the Coriolis force with a to Support member 18 directed toward force component can be acted upon, ie be deflected towards the annular gap 40 out.
  • the width MS of the annular gap 40 is adjustable, so that an adjustment to and an adaptation to the type and amount of the particles to be separated from the fluid is made possible.
  • the angle of attack indicated in the WA is none other than 90 ° and, depending on the nature of the fluid and the impurities contained therein and depending on the speed and / or flow speed in the fan wheel, is preferably between 45 and 80 °.
  • the angle of attack WA is chosen as a function of the particle size or the particle size distribution so that the particle separation receives a maximum.
  • additional blades 44 are offset to the fan blades 20 in the circumferential direction, in such a way that the deflected by the additional blades 44 particles under the influence of fluid mechanical and other dynamic forces do not hit the leading edges 24 of the fan blades 20 .
  • the additional blades 44 may also overlap in the radial direction with the Lüfterradschaufeln 20.
  • the auxiliary blades 44 have an axial extent EA that is less than the height H of the fan blades 20.
  • the auxiliary blades 44 have a height EA up to 50%, preferably up to 30%, of the axial extent H of the fan blades 20 is.
  • each fan blade 20 has on its working or pressure side at least one strip-like projection 48, which is employed to the flow direction in the flow channel 28 between the blades 20 such that the flow axially at least in Druckieridin axially on the support member 18th is deflected to and ends at a predetermined axial distance, which is preferably not greater than the dimension MS, to the support member 18.
  • two substantially mutually parallel projections 48a, 48b are provided on each Lüfterradschaufel 20, which in a substantially same axial distance MS - see FIG. 3 - End to the support member 18.
  • the strip-like projections 48 preferably have a height HLV - see FIG. 4 - Which is up to 50% of the axial extent H of the fan blades 20. Tests have shown that the height HLV of the strip-like projections should not exceed 8 mm.
  • the inclination angle WN under which the projections 48a, 48b are made to the blade surface 46, for example, set to 90 °.
  • this angle WN can be kept variable, for example, be much smaller than 90 °, the angle of attack or the surface design (also an arch shape is possible) of the projections 48 is determined empirically depending on the nature and consistency of the particles to be filtered out of the fluid.
  • the projections 48 are guided in the embodiment shown to the flow-leading edge 24 of the fan blades 24, but they can also end in front of the edge 24.
  • FIGS. 1 to 3 the additional blades 44 as well as the fan blades 20 are straight or flat.
  • FIGS. 5 and 6 a modification of the fan according to the invention is shown.
  • the blades 120 and 144 are curved, in the direction of rotation convex.
  • the fan blades 120 and / or the additional blades 144 may also be concave or S-shaped curved straight or in the direction of rotation of the fan.
  • FIGS. 5 and 6 is again equipped with the strip-like projections 148a, 148b. These can also be omitted - as in FIG. 7 is indicated by the dashed lines - or get another shape, for example, arcuate out, as that on the right side of FIG. 6 indicated by dashed lines.
  • the fan blades 20, 120 of the blade assembly may be normal to the plane the axis of rotation 12, ie to the plane of the support member 18, 118 at such an angle WS (see FIG. 4 ), which is smaller than 90 °, be employed, that in the fluid to be conveyed particles are acted upon with a support member 18 directed towards the force component.
  • This angle of attack WS can also vary in the radial direction. It has been found that the angle of attack WS is preferably selected such that: 90 ⁇ ° - WS ⁇ 90 ⁇ ° - WA ⁇ 2
  • the angle of attack WS of the fan blades is 75 °.
  • the fan blades 20 as well as the additional blades 44 made of sheet steel, wherein the material is tuned according to the ambient conditions in Einz the radial fan.
  • the material is tuned according to the ambient conditions in Einz the radial fan.
  • other materials can be used, depending on which properties are required in the long-term use.
  • the thickness of the fan blades 20, 120 and auxiliary blades 44, 144 is not shown to scale. Contrary to the Dartellung in the Figures 2 and 4 for example, the thickness D44 of the auxiliary blades is about three times the thickness D20 of the fan blades. That is, with a thickness D20 of the fan blades 20 of, for example, 5 mm (which is realistic for a fan of up to 1000 mm in diameter), the thickness D44 of the additional blades is about 15 mm. In this way, the different Verschl constitubealastened the blade groups is taken into account.
  • the invention thus provides an axial impinged radial impeller for conveying a particle laden fluid. It has a driven support member extending substantially perpendicular to an axis of rotation and carrying a vane assembly having a plurality of vane-like circumferentially spaced impeller vanes.
  • the fan blades each have a radially inward leading edge and a radially outer trailing edge. Radially outwardly directed flow channels are defined between the fan blades whereby an axial inlet flow can be deflected radially outwards.
  • the support member In order to effectively clean fluid laden with solid and / or liquid coarse particles as it flows through the fan, the support member has radially within the Lüfterradschaufeln additional axially projecting auxiliary blades from the support member, which are employed in the direction of rotation of the fan so that in the fluid to be conveyed particles with a force component directed towards the carrier part can be acted upon.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
EP08151624A 2007-02-26 2008-02-19 Roue de ventilateur radiale Withdrawn EP1961969A3 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP08151624A EP1961969A3 (fr) 2007-02-26 2008-02-19 Roue de ventilateur radiale

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
EP07003875A EP1961966A1 (fr) 2007-02-26 2007-02-26 Roue de ventilateur radiale
EP07022327 2007-11-16
EP08151624A EP1961969A3 (fr) 2007-02-26 2008-02-19 Roue de ventilateur radiale

Publications (2)

Publication Number Publication Date
EP1961969A2 true EP1961969A2 (fr) 2008-08-27
EP1961969A3 EP1961969A3 (fr) 2009-10-21

Family

ID=39377058

Family Applications (1)

Application Number Title Priority Date Filing Date
EP08151624A Withdrawn EP1961969A3 (fr) 2007-02-26 2008-02-19 Roue de ventilateur radiale

Country Status (1)

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EP (1) EP1961969A3 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2143958A1 (fr) 2008-07-07 2010-01-13 Josip Pavetic Ventilateur installé dans un tuyau
ITFI20120125A1 (it) * 2012-06-19 2013-12-20 Nuovo Pignone Srl "wet gas compressor and method"
CN103939391A (zh) * 2014-04-18 2014-07-23 林钧浩 支叶片加固增压通风机

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1503650A1 (de) 1965-12-23 1969-03-13 Meissen Turbowerke Ventilatorlaufrad zur Foerderung staubhaltiger Gase
EP0615069A1 (fr) 1993-03-09 1994-09-14 RATIONAL GmbH Roue de ventilateur
DE10315341B4 (de) 2003-04-03 2005-04-14 Mkn Maschinenfabrik Kurt Neubauer Gmbh & Co. Gargerät mit einem Gebläse mit Radialgebläserad und Abscheideelement
EP1530682B1 (fr) 2002-08-22 2006-05-31 Rational AG Roue de ventilateur pourvue d'une separation de graisse integree et destinee notamment a un appareil de cuisson

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE607157C (de) * 1932-10-19 1934-12-18 Schiele & Co G M B H G Fluegelrad zu Kreiselgeblaesen fuer die Befoerderung von Luft mit festen Bestandteile
US3104050A (en) * 1960-08-17 1963-09-17 Richard W Coward Blades for centrifugal fans and the like
DE2809597A1 (de) * 1978-03-06 1979-10-04 Konrad Reitz Maschinen U Appar Radial-ventilator
GB2225814B (en) * 1988-12-06 1993-03-24 Johnston Eng Ltd Fan impellers for road sweeping vehicles

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1503650A1 (de) 1965-12-23 1969-03-13 Meissen Turbowerke Ventilatorlaufrad zur Foerderung staubhaltiger Gase
EP0615069A1 (fr) 1993-03-09 1994-09-14 RATIONAL GmbH Roue de ventilateur
EP1530682B1 (fr) 2002-08-22 2006-05-31 Rational AG Roue de ventilateur pourvue d'une separation de graisse integree et destinee notamment a un appareil de cuisson
DE10315341B4 (de) 2003-04-03 2005-04-14 Mkn Maschinenfabrik Kurt Neubauer Gmbh & Co. Gargerät mit einem Gebläse mit Radialgebläserad und Abscheideelement

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2143958A1 (fr) 2008-07-07 2010-01-13 Josip Pavetic Ventilateur installé dans un tuyau
ITFI20120125A1 (it) * 2012-06-19 2013-12-20 Nuovo Pignone Srl "wet gas compressor and method"
WO2013189945A1 (fr) * 2012-06-19 2013-12-27 Nuovo Pignone Srl Compresseur à gaz humide et procédé
CN104641120A (zh) * 2012-06-19 2015-05-20 诺沃皮尼奥内股份有限公司 湿气压缩机和方法
RU2614309C2 (ru) * 2012-06-19 2017-03-24 Нуово Пиньоне СРЛ Компрессор влажного газа и способ
US9890787B2 (en) 2012-06-19 2018-02-13 Nuovo Pignone Srl Wet gas compressor and method
CN104641120B (zh) * 2012-06-19 2018-09-21 诺沃皮尼奥内股份有限公司 湿气压缩机和方法
CN103939391A (zh) * 2014-04-18 2014-07-23 林钧浩 支叶片加固增压通风机

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Publication number Publication date
EP1961969A3 (fr) 2009-10-21

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