EP1961970A1 - Roue de ventilateur radial et ventilateur radial équipé de celle-ci doté d'une protection contre la fermeture - Google Patents

Roue de ventilateur radial et ventilateur radial équipé de celle-ci doté d'une protection contre la fermeture Download PDF

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Publication number
EP1961970A1
EP1961970A1 EP08151626A EP08151626A EP1961970A1 EP 1961970 A1 EP1961970 A1 EP 1961970A1 EP 08151626 A EP08151626 A EP 08151626A EP 08151626 A EP08151626 A EP 08151626A EP 1961970 A1 EP1961970 A1 EP 1961970A1
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EP
European Patent Office
Prior art keywords
fan
blades
radial
flow
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Withdrawn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
EP08151626A
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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
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Filing date
Publication date
Application filed by Individual filed Critical Individual
Priority to EP08151626A priority Critical patent/EP1961970A1/fr
Publication of EP1961970A1 publication Critical patent/EP1961970A1/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Withdrawn legal-status Critical Current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 inner leading edge and a radially outer outlet edge and between which radially outwardly directed flow channels are fixed, whereby an axial inlet flow (SE) is deflected radially outward. according to the preamble of claim 1.
  • SE axial inlet flow
  • Such fan wheels are for example from the documents EP 0615069 A1 .
  • the impellers described above are primarily used where it is necessary to pump fluid from an environment that is loaded with substantial quantities of solid and / or liquid particles.
  • the radial fan equipped with the fan has on the side facing away from the carrier part an inlet for the fluid and the fan carries a blade assembly in the form of a blade ring, between the individual blades radial channels are defined by the radially outwardly deflected from the axial direction fluid to the outside flow and can escape from the impeller there.
  • 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 abrasive materials, such as solid or suspended water droplets or dust particles loaded.
  • 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. So that the expense of depositing the particles can be kept small and yet the separation and delivery efficiency at a high level, the fan wheels are given the task to effectively deposit these particles - at least in part - as it flows through the fan before exiting the fan.
  • the invention is therefore the object of developing a radial impeller of the type described above in such a way that the service life can be significantly increased, especially if the fluid to be pumped are loaded with abrasive particles.
  • the support member is fitted radially within the fan blades with additional axially projecting from the support member additional blades, which are employed to the normal plane of the rotation axis such that in the fluid to be delivered Particles are acted upon with a directed away from the carrier part force component. It could be shown in tests that the service life of the fan wheel can be increased by 2 to 5 times with this measure.
  • the flow characteristics of the fan can be improved.
  • auxiliary blades are circumferentially offset to the fan blades or even overlap with the fan blades in the radial direction, further improved protection of the fan blades from wear occurs.
  • the additional blades may have a height that varies in the radial direction. In this way, the fluidic losses are minimized.
  • the service life of the fan wheel can be further increased.
  • the additional blades are interchangeable, so that the life of the fan is further improved.
  • Another measure for increasing the service life of the radial impeller is to make the thickness or the sheet thickness of the additional blades larger than that of the fan main blades, for example by a factor of 3.
  • the auxiliary blades have a maximum axial extent which is less than that of the fan blades, whereby the flow losses can be further reduced.
  • a radial fan according to the invention which is equipped with a fan according to the invention is the subject of claims 14 to 17.
  • This radial fan can simultaneously deposit a variable percentage of solid or liquid particles contained in the fluid through the annular channel with the outlet.
  • the radial fan can be optimally adapted to the quality of the fluid to be delivered.
  • the invention can be combined with various designs of the fan wheel, including those in which the fan wheels an improved separation efficiency is transmitted.
  • the fan blades can be adjusted to the normal plane of the rotation axis at such an angle or obliquely that in the Particles to be delivered fluid can be acted upon under the influence of centrifugal and Coriolis force with a force component directed towards the carrier part.
  • 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. If the angle of attack of the fan blades with respect to the normal plane to the axis of rotation varies in the radial direction, the deposition effect can be further optimized.
  • the impeller according to the invention operates quieter and with a higher fluidic efficiency, as equipped with additional fins fan wheels, and yet not prone to local particle accumulation, which can be hearbmaj the maintenance.
  • the fan according to the invention is also suitable for the coarse 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.
  • 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.
  • these projections small liquid particles can be deposited effectively. Due to the additional blades according to the invention, it is possible to effectively control the wear on such projections, even if the height of the projections should be considerable. However, if the height H is in the mm range, the noise can be limited and at the same time a better efficiency can be achieved.
  • 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 reference numeral 10 generally designates an axially impinged radial impeller which serves to convey a fluid or fluid, in particular a fluid laden with solid or liquid particles.
  • a fluid or fluid in particular a fluid laden with solid or liquid particles.
  • Such a fan can be used for example in a radial fan, which in FIG. 5 is shown schematically.
  • the impeller 10 is intended to be capable of handling fluids, in particular gaseous fluids, which may interfere with abrasive particles, e.g. Dust particles, water particles, snowflakes, fat particles and the like. Are loaded to pump effectively or pump out of an environment.
  • abrasive particles e.g. Dust particles, water particles, snowflakes, fat particles and the like.
  • Such fan wheels can also fulfill the task of largely separating these particles during the flow of the fan impeller.
  • a specific field of application of the fan wheel is in the conveying / filtering function of fluids which have an extremely high proportion of entrained particles, wherein the wear on the fan wheel should be as low as possible.
  • the fan 10 has a rotation axis 12, which - as can be seen from the FIG. 5 recognizes, which should already be referred to here - in the assembly in one Fan housing 14, for example, vertically aligned.
  • the orientation of the axis 12 is arbitrary.
  • 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 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 FIGS. 1 and 4 yields - to an axis of rotation 12 containing axial plane 22, such as the plane of the FIG. 3 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 are aligned parallel to the axis of rotation 12, but they can also be employed to the normal plane 15, which coincides in the embodiment shown with the plane of the support member 18, at an angle ⁇ 90 °, ie such that contained in the fluid to be conveyed particles under the influence of the dynamic forces, including the centrifugal and the Coriolis forces, are acted upon with a force component directed towards the support member.
  • the fan blades 20 are straight. However, it should already be emphasized at this point that the blade shape can be modified as desired in order to improve the fluidic efficiency of the fan and / or the particle separation to be described later.
  • the fan blades 20 each have a radially inner leading edge 24 and a radially outer trailing edge 26. Between the fan blades 20 substantially radially outwardly directed flow channels 28 are defined, so that therefore an axial inlet flow - in FIG. 5 denoted by the arrow SE - is at radially rotating fan 10 radially outward in an outlet flow SA with radial and directed in the circumferential direction speed 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. 3 ) or 229 (see FIG. 5 ).
  • the blades carry on the side facing away from the support member 18, an annular disc 21 and they are firmly connected to this, for example, welded. You can also 20 just below a top wall of the housing 14 ends.
  • the axial extent H of the fan blades 20 thus determined as a distance between the support member 18 and the 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.
  • a freely cantilevered shape of the blades has the advantage that no particle accumulations are formed in the fan.
  • the fan 10 is installed in the housing 14 of the Radialgebläseso that it comes to rest below an axial inlet funnel or inlet nozzle 30 which is aligned with the axis of rotation 12 of the fan 10. Radially from the outside, the fan 10 is enclosed by an annular channel 32 having an outlet 34 for the fluid.
  • 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 additional blades 44 are employed against the direction of rotation V, ie they close with the normal plane 15 to the axis of rotation 12 and with the plane of the support member 18 at an angle WA> 90 °, which manages the wear of the fan blades 20 and possibly attached thereto strip-like projections in FIG. 1 indicated only by dashed lines and designated by 48, to even.
  • the angle of attack WA can be up to 135 ° and is selected as a function of the particle size, weathering and consistency as well as the flow velocities in order to minimize the wear of the main blades.
  • the additional blades 44 have an axial extent EA, which is less than the height H of the fan blades 20.
  • the additional blades 44 have a height EA, which is up to 50%, preferably up to 30% of the axial extent H of the fan blades 20.
  • 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 blades 20 and 44 are subject to different wear, so it is advantageous to keep the thickness D44 of the auxiliary blades larger than the thickness D20 of the main blades 20.
  • the thickness of the fan blades 20, 120 and auxiliary blades 44, 144 not reproduced to scale. Contrary to the Dartellung in the Figures 2 and 3
  • the thickness D44 of the auxiliary blades 44 is about three times the thickness D20 of the fan blades. That is, at a thickness D20 of the fan blades 20, for example, 5 mm (which is realistic for a fan of up to 1000 mm diameter) is the thickness D44 of the additional blades about 15 mm.
  • 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.
  • each fan blade 20 can carry on its working or pressure side 46 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 Druckhowmony to the support member 18 is deflectable and at a predetermined axial distance, preferably not greater than the dimension MS - see FIG. 5 - is, to the support member 18 ends.
  • a strip-like projection 48 is provided at all, its height is kept rather small and should not exceed the dimension of 8 mm.
  • the fan blades 120 are convex in the direction V.
  • the Lüfterradschaufeln 120 are smooth, so that there is a good efficiency and low noise.
  • each Lüfterradschaufel 220 namely on the respective working or printing side 246 two substantially mutually parallel strip-like projections 248a, 248b provided that terminate at a substantially same axial distance MS to the support member 218.
  • An unillustrated angle of inclination, under which the projections 248a, 248b are made to the blade surface 246, can be set to a certain value, which is the composition of the fluid best in terms of wear minimization and / or Abscheide Angelsgrad.
  • the angle of attack or the surface design (also an arch shape is possible) of the protrusions 248 is preferably determined empirically depending on the type and consistency of the particles to be filtered out of the fluid.
  • the projections 248 are in the embodiment shown to the flow-leading edge 224 of the Lüfterradschaufeln 220 out, but they can also end in front of the edge 224.
  • the fan blades 20 can also be made at an angle WS, which is smaller than 90 ° to the peripheral velocity vector, whereby the particles contained in the fluid, which may be in solid or liquid form, under the influence of the fluidic forces, the inertial forces and the other dynamic Forces such as centrifugal and Coriolis forces are urged towards the support member 18, so that in the area radially inside the annular gap 40 a significantly larger particle concentration is present than in the rest of the flow.
  • 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.
  • Ach the angle of attack WS of the fan blades 20, 120, 220 can be varied with respect to the normal plane 15 to the axis of rotation 12 in the radial direction, so that there is a kind of propeller shape for the blades.
  • the additional blades 144 as well as the fan blades 120 are convex. But they can also be straight or concave or S-shaped.
  • the strip-like projections 248a, 248b may also or be given a different shape, for example, be guided arcuately.
  • the invention thus provides 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 assembly with a plurality of annularly spaced circumferentially spaced impeller blades, each having a radially inward leading edge and a radially outer outlet edge and between which radially outwardly directed flow channels are fixed, whereby a axial inlet flow can be deflected radially outwards.
  • the support carries radially within the fan blades additional axially projecting from the support member supporting blades, which are employed to the normal plane of the rotation axis such that in the fluid to be conveyed particles with a force component directed away from 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)
EP08151626A 2007-02-26 2008-02-19 Roue de ventilateur radial et ventilateur radial équipé de celle-ci doté d'une protection contre la fermeture Withdrawn EP1961970A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP08151626A EP1961970A1 (fr) 2007-02-26 2008-02-19 Roue de ventilateur radial et ventilateur radial équipé de celle-ci doté d'une protection contre la fermeture

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
EP07003877A EP1961968A1 (fr) 2007-02-26 2007-02-26 Roue de ventilateur radial et ventilateur radial équipé de celle-ci doté d'une protection contre la fermeture
EP08151626A EP1961970A1 (fr) 2007-02-26 2008-02-19 Roue de ventilateur radial et ventilateur radial équipé de celle-ci doté d'une protection contre la fermeture

Publications (1)

Publication Number Publication Date
EP1961970A1 true EP1961970A1 (fr) 2008-08-27

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Family Applications (2)

Application Number Title Priority Date Filing Date
EP07003877A Withdrawn EP1961968A1 (fr) 2007-02-26 2007-02-26 Roue de ventilateur radial et ventilateur radial équipé de celle-ci doté d'une protection contre la fermeture
EP08151626A Withdrawn EP1961970A1 (fr) 2007-02-26 2008-02-19 Roue de ventilateur radial et ventilateur radial équipé de celle-ci doté d'une protection contre la fermeture

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Application Number Title Priority Date Filing Date
EP07003877A Withdrawn EP1961968A1 (fr) 2007-02-26 2007-02-26 Roue de ventilateur radial et ventilateur radial équipé de celle-ci doté d'une protection contre la fermeture

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Families Citing this family (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
DE102015213006A1 (de) * 2015-07-10 2017-01-12 Mahle International Gmbh Gebläseanordnung
CN106837823B (zh) * 2017-03-06 2023-06-20 昆山佰斯拓机械设备有限公司 带圆柱降噪结构的多叶离心通风机及其降噪流程

Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1739604A (en) * 1927-02-14 1929-12-17 Clarage Fan Company Fan
FR1058690A (fr) 1951-07-21 1954-03-18 Babcock & Wilcox France Roue pour machine soufflante radiale
GB894893A (en) 1958-07-08 1962-04-26 Svenska Flaektfabriken Ab Improvements in centrifugal fans
US3104050A (en) 1960-08-17 1963-09-17 Richard W Coward Blades for centrifugal fans and the like
DE1503650A1 (de) * 1965-12-23 1969-03-13 Meissen Turbowerke Ventilatorlaufrad zur Foerderung staubhaltiger Gase
DE2809597A1 (de) * 1978-03-06 1979-10-04 Konrad Reitz Maschinen U Appar Radial-ventilator
EP0372701A1 (fr) 1988-12-06 1990-06-13 Johnston Engineering Limited Dispositifs de balayage des rues
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

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1739604A (en) * 1927-02-14 1929-12-17 Clarage Fan Company Fan
FR1058690A (fr) 1951-07-21 1954-03-18 Babcock & Wilcox France Roue pour machine soufflante radiale
GB894893A (en) 1958-07-08 1962-04-26 Svenska Flaektfabriken Ab Improvements in centrifugal fans
US3104050A (en) 1960-08-17 1963-09-17 Richard W Coward Blades for centrifugal fans and the like
DE1503650A1 (de) * 1965-12-23 1969-03-13 Meissen Turbowerke Ventilatorlaufrad zur Foerderung staubhaltiger Gase
DE2809597A1 (de) * 1978-03-06 1979-10-04 Konrad Reitz Maschinen U Appar Radial-ventilator
EP0372701A1 (fr) 1988-12-06 1990-06-13 Johnston Engineering Limited Dispositifs de balayage des rues
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

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