EP1961967A1 - Roue de ventilateur radial et ventilateur radial équipé de celle-ci - Google Patents

Roue de ventilateur radial et ventilateur radial équipé de celle-ci Download PDF

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Publication number
EP1961967A1
EP1961967A1 EP07003876A EP07003876A EP1961967A1 EP 1961967 A1 EP1961967 A1 EP 1961967A1 EP 07003876 A EP07003876 A EP 07003876A EP 07003876 A EP07003876 A EP 07003876A EP 1961967 A1 EP1961967 A1 EP 1961967A1
Authority
EP
European Patent Office
Prior art keywords
fan
blades
fan wheel
support member
wheel according
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Withdrawn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
EP07003876A
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German (de)
English (en)
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
Application filed by Individual filed Critical Individual
Priority to EP07003876A priority Critical patent/EP1961967A1/fr
Publication of EP1961967A1 publication Critical patent/EP1961967A1/fr
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/26—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 according to the preamble of patent claim 1.
  • Such fan wheels are for example from the documents EP 0615069 A1 .
  • Such a fan wheel has on the side facing away from the carrier part an inlet section for the fluid and a blade arrangement in the form of a blade ring, between the individual blades radial channels are defined, through which the fluid radially deflected from the axial direction flow to the outside and there from the impeller can escape.
  • the impeller is usually installed in a blower housing with such a fit that it is surrounded by an annular channel with an outlet.
  • the fluids or fluids to be delivered by such radial fans are loaded with substances, for example with liquid or solid particles, such as water or fat droplets or dust particles.
  • substances for example with liquid or solid particles, such as water or fat droplets or dust particles.
  • filters can always be upstream or downstream. But these filters have the disadvantage that they must be maintained consuming to keep the pressure drop in the flow within tolerable limits.
  • the fan wheels is transferred the task of effectively segregating these particles as they flow through the fan before exiting the fan.
  • the invention is therefore based on the object, a radial impeller of the type described above in such a way that it has a particularly good deposition efficiency for such fluids or fluids that have a particularly high particle load.
  • the blades of the fan-blade assembly are set to the normal plane of the rotation axis at such an angle or inclined that contained in the fluid to be conveyed particles under the influence of centrifugal and Coriolis with a force directed towards the carrier part force component can be acted upon.
  • the particles contained in the fluid during flow through the fan or the trained between the Lüferradschaufeln flow channels are urged directly into the area near the support member, so that they at the radially outer end of the support member, ie when leaving the fan, on the separation annular gap can be separated from the fluid flow. It has been shown in experiments that with extremely highly particle-loaded fluids separation efficiencies can be achieved, which are far above those which could be realized with conventional constructions.
  • the impeller according to the invention operates quieter and with a higher fluidic efficiency, as the equipped with additional fins fan wheels, and not to local particle accumulation tends, which can be hearbitch the maintenance.
  • the fan according to the invention is also suitable for the cleaning of fluids that are loaded with a mix of liquid and solid particles.
  • the blades of the blade assembly form a blade ring with radially inward flow inlet edges and radially outer flow outlet edges, wherein the flow inlet edges and flow outlet edges each having a pitch circle associated, there is a rotationally symmetrical structure of the fan, whereby the manufacturing cost can be reduced ,
  • flow inlet edges extend from a hub portion of the carrier part axially away from the latter to a blade edge extending essentially parallel to the carrier part, a flow channel which is favorable for the fluid flow and has a substantially constant height in the radial direction results, a particularly compact form of the fan, which can be installed with little effort in a fan housing.
  • Straight or non-curved blades have advantages in terms of ease of maintenance in certain particle sizes and / or distributions, since they counteract the tendency to particle deposits.
  • a particularly high degree of fluid-mechanical efficiency of the fan wheel results if the blades are curved in a convex manner in the direction of rotation of the fan wheel.
  • the impeller may additionally be modified to the effect that each impeller blade receives on its working or pressure side at least a strip-like projection which is employed to the flow direction in the flow channel between the blades such that the flow is axially deflectable at least in printing side proximity to the support member, wherein the strip-like projection terminates at a predetermined and small axial distance from the carrier part.
  • the strip-like projection terminates at a predetermined and small axial distance from the carrier part.
  • the support member may radially within the Lüfterradschaufeln also carry a further blade ring with the carrier part projecting additional blades, wherein the axial extent of the additional blades is preferably less than that of the fan blades. With this measure, particularly large particles can be deposited effectively.
  • the carrier part is formed by a plate, the construction of the fan wheel and thus of the radial fan is further simplified, with the particular advantage that the carrier part in operation does not tend to particle accumulations on its top.
  • the stability of the fan can be raised, with the result that the support member and / or the hub are made easier and a compound of the fan blades can be omitted with the hub.
  • the deposition effect can be optimized.
  • the reference numeral 10 generally denotes an axially impinged radial impeller, which serves for conveying a fluid or fluid, in particular a laden with solid or liquid particles fluid.
  • the fan 10 should be able to largely separate the particles, such as dust particles, water particles, snowflakes, fat particles and the like., When flowing through the fan.
  • the specific field of application of the fan wheel is in the filtering function of fluids that have an extremely high proportion of entrained particles.
  • the fan 10 has a rotation axis 12, which - as can be seen from the FIGS. 1 and 2 recognizes - when mounting in a fan 14, for example, vertically aligned.
  • the orientation of the axis 12 is arbitrary.
  • a designated 16 hub rotatably seated on a drive shaft 13 with the axis 12 and it carries a blade support member 18 which extends substantially perpendicular to the axis of rotation 12.
  • the carrier part 18, in turn, carries a blade arrangement with a large number of fan wheel blades 20 arranged in the manner of a wreath at a circumferential distance from each other and, as a rule, identically designed.
  • the fan blades 20 are - as is apparent from the illustrations of Figures 3 and 4 results, to which extent already taken so far - to an axis of rotation 12 containing axial plane 22, such as the plane of the FIG. 2 at a certain angle DELTA, so that they produce a radially outward flow when turning the fan 10 with the direction of rotation V.
  • the angle DELTA can also be NULL.
  • the fan blades - as is apparent from the FIG. 2A results - not aligned parallel to the axis of rotation 12, but they are to the normal plane 15, which coincides in the embodiment shown with the plane of the support member 18, at an angle WS ⁇ 90 °, ie adjusted so that contained in the fluid to be conveyed under the influence of the dynamic forces, including the centrifugal and the Coriolis forces, are acted upon by a force component directed towards the carrier part.
  • FIG. 1 the Figures 1 to 2A are the fan blades 20 straight, resulting from the FIG. 1 results.
  • the blade shape can be modified as desired can to improve the fluid dynamics of the fan and / or the later to be described particle deposition.
  • 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.
  • leading edges 24 and flow outlet edges 26 each have a pitch circle 24a or 26a associated therewith.
  • 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. 1 ).
  • the shape of the Lüfterradschaufeln 20 can - depending on the fan design - vary within wide limits. If the fan blades 20 - as in FIG. 2 shown - wear a dimensionally stable washer 21, the construction of the fan is stiffer, so that it is sufficient to attach the fan blades on the support member 18, such as welding. The leading edge 24 of the fan blades can then be arranged substantially parallel to the axis of rotation. On the other hand, the cantilevered shape of the blades after FIG. 1 the advantage that no particles accumulate in the fan.
  • the fan 10 is installed in the housing 14 of the radial fan so that it is below an axial inlet funnel or inlet nozzle 30, which is in alignment with the axis of rotation 12 of the fan 10 comes. 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 while maintaining a small gap 37.
  • 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 18 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 highly particulate laden fluid preferably gaseous fluid, such as air
  • gaseous fluid such as air
  • the particles contained in this ströungs slaughter reach via the annular gap 40 in the annular chamber 42, which is preferably designed so that no excessive back pressure is built up therein.
  • the main flow leaving the fan 10 above the annular gap 40 is cleaned to a correspondingly high percentage.
  • the adjustability of the measure MS can be influenced by the degree of separation efficiency as a function of the composition of the fluid to be cleaned.
  • each fan blade 20 on its working or pressure side 46 carry at least one strip-like projection 48 to the flow direction in the flow channel 28 between the blades 20th is set so that the flow is axially deflected at least in printing side proximity axially on the support member 18 and which ends at a predetermined axial distance, which is preferably not greater than the dimension MS to the support member 18.
  • each Lüfterradschaufel 20 two substantially mutually parallel projections 48a, 48b are provided, which in a substantially same axial distance MS - see FIG. 2 - End to the support member 18.
  • the strip-like projections 48 preferably have a low height HLV FIG. 2A - which can be in the millimeter range, so that the flow losses do not increase. But it can also be up to 50% of the axial extent H of the fan blades 20.
  • the inclination angle WN under which the projections 48 are made to the blade surface 46, set to an angle which is smaller than 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 20, but they can also end before the edge 24.
  • the fan 110 after FIG. 3 has in the direction of rotation V convex curved Lüfterradschaufeln 120, which are employed in the direction of rotation V.
  • the fan blades 120 may be provided with - not shown - strip-like projections 148.
  • additional blades 144 may be attached, wherein the axial extent of the additional blades is less than that of the fan blades 120.
  • the additional blades 144 are in the embodiment according to FIG. 3 is made against the direction of rotation V, which makes it possible to even out the wear of the fan blades 120 and possibly attached thereto projections 148.
  • auxiliary blades 144 are circumferentially offset to the fan blades 120 in such a way that the particles deflected by the auxiliary blades 144 do not strike the leading edges 124 of the fan blades 120 under the influence of fluidics and other dynamic forces .
  • the auxiliary blades 144 may also overlap in the radial direction with the fan blades 120.
  • the additional blades 244 in the direction of rotation V of the fan 10 so employed that contained in the fluid to be conveyed particles under the action of the impulse force, the centrifugal force and the Coriolis force with a directed to the support member 18 towards force component can be acted upon, ie be deflected towards the annular gap 40 out ,
  • the fluid flowing in at 30 can be efficiently cleaned during the passage of the radial fan of very coarse or heavy solid or liquid particles.
  • the additional blades can also be substantially vertical on the normal plane to the rotation axis 212 or on the plane of the support part 218.
  • the angle of attack WS of the fan blades 20, 120, 220 with respect to the normal plane 15 can be varied in the radial direction relative to the axis of rotation 12, so that a kind of propeller shape results for the blades.
  • the additional blades 144, 244 as well as the Lüfterradschaufeln 120, 220 are designed convex. But they can also be straight or concave or S-shaped.
  • the strip-like projections 48a, 48b may also or obtain another shape, for example, be guided arcuately.
  • the invention thus provides an axial impinged radial impeller for a radial fan which serves to convey and concurrently purify fluid having high concentrations of liquid and / or solid particles. It has a driven support part which extends substantially perpendicular to a rotation axis and carries a blade arrangement, with which a substantially axially directed inlet flow can be deflected radially outwards.
  • the blades of the blade assembly are adjusted to the normal plane of the axis of rotation at such an angle WS that the particles contained in the fluid to be delivered can be acted upon by flowing through the fan with a force component directed towards the support member, so that sets a much higher particle concentration near the support member.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
EP07003876A 2007-02-26 2007-02-26 Roue de ventilateur radial et ventilateur radial équipé de celle-ci Withdrawn EP1961967A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP07003876A EP1961967A1 (fr) 2007-02-26 2007-02-26 Roue de ventilateur radial et ventilateur radial équipé de celle-ci

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP07003876A EP1961967A1 (fr) 2007-02-26 2007-02-26 Roue de ventilateur radial et ventilateur radial équipé de celle-ci

Publications (1)

Publication Number Publication Date
EP1961967A1 true EP1961967A1 (fr) 2008-08-27

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Family Applications (1)

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EP07003876A Withdrawn EP1961967A1 (fr) 2007-02-26 2007-02-26 Roue de ventilateur radial et ventilateur radial équipé de celle-ci

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Cited By (4)

* 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
WO2012080012A1 (fr) * 2010-12-14 2012-06-21 Voith Patent Gmbh Ventilateur radial doté d'une fonction de séparation des gouttes
DE102015213006A1 (de) * 2015-07-10 2017-01-12 Mahle International Gmbh Gebläseanordnung
CN108114542A (zh) * 2018-01-10 2018-06-05 林德祥 净化装置单元及净化装置

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1232697B (de) * 1962-04-05 1967-01-19 Babcock & Wilcox Dampfkessel Geblaeseschaufelrad fuer die Foerderung staubhaltiger Gase
US6846157B1 (en) 2003-09-24 2005-01-25 Averatec Inc. Cooling fans
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

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1232697B (de) * 1962-04-05 1967-01-19 Babcock & Wilcox Dampfkessel Geblaeseschaufelrad fuer die Foerderung staubhaltiger Gase
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
US6846157B1 (en) 2003-09-24 2005-01-25 Averatec Inc. Cooling fans

Cited By (5)

* 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
WO2012080012A1 (fr) * 2010-12-14 2012-06-21 Voith Patent Gmbh Ventilateur radial doté d'une fonction de séparation des gouttes
DE102015213006A1 (de) * 2015-07-10 2017-01-12 Mahle International Gmbh Gebläseanordnung
CN108114542A (zh) * 2018-01-10 2018-06-05 林德祥 净化装置单元及净化装置
CN108114542B (zh) * 2018-01-10 2024-05-28 林德祥 净化装置单元及净化装置

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