EP2143958A1 - Ventilateur installé dans un tuyau - Google Patents

Ventilateur installé dans un tuyau Download PDF

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Publication number
EP2143958A1
EP2143958A1 EP08012256A EP08012256A EP2143958A1 EP 2143958 A1 EP2143958 A1 EP 2143958A1 EP 08012256 A EP08012256 A EP 08012256A EP 08012256 A EP08012256 A EP 08012256A EP 2143958 A1 EP2143958 A1 EP 2143958A1
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EP
European Patent Office
Prior art keywords
fan
blades
der
die
flow
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.)
Pending
Application number
EP08012256A
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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 EP08012256A priority Critical patent/EP2143958A1/fr
Priority to CN200910211631A priority patent/CN101699076A/zh
Publication of EP2143958A1 publication Critical patent/EP2143958A1/fr
Pending 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
    • 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

Definitions

  • the invention relates to a built-in a pipe and in the axial direction promotional, driven by a motor fan.
  • Such fans are known in many types. In general, however, such fans are formed by axial fans or axial fans, which suck in a flow axially and further promote in the axial direction.
  • media that must be conveyed in the pipe are loaded with particles in solid and / or liquid form. These may be fat particles, dust particles or even snow or the like. If conventional fans are installed in such a piece of pipe, the fan must be preceded by filters upstream or downstream, to effectively separate such particles from the flow. However, such filters reduce the efficiency of fluid delivery, which can be maintained at a tolerable level anyway only if such filters are frequently changed or cleaned.
  • the invention is therefore based on the object to provide an arrangement with which it is possible to promote a particle-laden flow in a pipe in such a way that with low space requirements, the particles contained in the flow can be effectively separated.
  • an axially sucking and radially conveying fan wheel is installed in the tube, which is designed in a special way and adapted to a collecting groove surrounding the fan wheel, so that it succeeds solely by the rotational movement of the fan a large part of the particles contained in the fluid to be delivered to feed the circumferential gap of the collecting channel and from there with accordingly derive high speed. It has been found that such a fan, even if the outlet edges of the blades are on a pitch circle which is slightly smaller than that in the diameter of the tube, a sufficiently stable and still relatively lossless flow in the tube is stabilized, but at the same time the fan is reliable in a position to the particles contained in the fluid, such.
  • the flow with which the particles are discharged be accelerated by means of an additional pump.
  • An additional advantage of the invention is that the built-in tube fan can be designed as a module that can be installed to save space in an existing pipe system, so that complex redesigns are avoided.
  • the efficiency of particle separation can be further improved noticeably without having to raise the pressure loss when flowing through the pipe excessively. It has been found that the flow exiting the fan wheel, regardless of the orientation of the tube axis, still has a sufficiently large peripheral speed to be due to the centrifugal force in cooperation with the at least one sectionally helical groove on the tube inner wall to ensure that the particles can be trapped in the channel and taken from the flow system via the particle discharge channel section.
  • a particularly simple construction of the cleaning system is achieved when the particle discharge pipes simultaneously form the particle removal channel sections for the channel.
  • This suction is therefore particularly reliable because the flow rate in the particle discharge pipes can easily be in the range of 50 m / s.
  • the particular advantage is that the cleaning device does not require a filter and the fan with particle separator and motor takes up relatively little space.
  • the collection trough closely conforms to the radially outer blade edges, preferably in such a way that only a gap of a size in the mm range results between the collecting trough and an edge section, the yield in the particle separation can be further increased. It succeeds with relatively little manufacturing effort to comply with this small gap in the mm range even if fan wheels with a diameter of 300 to 500 mm are used.
  • claim 6 has the particular advantage that the particle discharge pipes, over which the fan and motor is held on the pipe, can be kept relatively short. This contributes to the stability of the fan assembly.
  • About the radius, i. the bending section of the particulate discharge tubes may provide a smooth transition of the particle flow from a radially directed flow to an axially directed flow in the second section of the particulate discharge tubes, thereby minimizing the risk of deposits and concomitant pressure losses in the particulate discharge flow.
  • the tube can therefore run horizontally or vertically without noticeably changing the efficiency.
  • a particularly stable and at the same time the flow in the pipe as little hindering structure of the arrangement is the subject of claim 7. Due to the tangential connection of the particle discharge pipes to the collecting channel is still the peripheral velocity of the particles to 100% in the outflow velocity of the particles in the particle Removal pipes implemented. Because a plurality of helical grooves are provided on the inner wall of the pipe section, particles can be trapped over the entire circumference on a shortened axial distance, so that the axial space of the arrangement can be further reduced.
  • the pitch angle of the helical grooves is usually selected as a function of the flow conditions in the tube, taking into account the peripheral speed of the fan. First results show that pitch angles in the range between 5 ° and 30 ° are achieved.
  • the particle discharge pipes alone can take over the task of mounting the motor with the fan.
  • the development of claim 8 has the advantage that the particle discharge pipes can be optimized in terms of their design and orientation in space with regard to an optimal flow of the particles, without having to take into account the stabilizing function of the fan in the pipe consideration.
  • the inlet funnel according to claim 9 can be used in an advantageous manner to keep the fluid flow in the pipe even lossless. This not only affects the inlet flow of the fan, but also the design of the dead space between the inlet opening of the tube and the outlet edge of the fan.
  • the arrangement can be easily incorporated into all existing pipe systems, for example, by using a section of the existing channel system and extended by the attachment of ring flanges.
  • the fan-blade assembly has blades that are tilted at such an angle of attack that the particles contained in the fluid to be delivered are subjected to a force component directed toward the carrier member under the influence of the centrifugal force and the Coriolis force ,
  • This fan is particularly advantageous when it comes to fluids that are extremely high loaded with particles.
  • This fan has the further advantage that it works with a relatively high flow efficiency.
  • the fan wheel is therefore particularly suitable for the cleaning of fluids that are loaded with a mix of liquid and solid particles.
  • a further embodiment of the fan wheel according to claim 12 provides that the support member carries radially within the Lüfterradschaufeln additional, axially projecting from the support member additional blades. These can be made, for example, to the normal plane of the rotation axis such that particles contained in the fluid to be delivered can be acted upon by a force component directed away from the carrier part. This measure has the advantage that a certain amount of wear protection is provided for flows that are heavily loaded with particles.
  • auxiliary blades in order to further increase the deposition efficiency in fluid flows, it is advantageous to start the auxiliary blades according to claim 13.
  • the fan is so according to this development just at the point where the flow velocity of the fluid is relatively small, equipped with additional blades that are used, primarily heavy particles in the fluid, which can not join the deflection of the flow due to their inertia, radially to promote to the outside, namely that point of the fan on which the separation ring gap is located.
  • coarse particles loaded fluid can be cleaned in this way with an improved efficiency, even if it is dispensed with additional measures for particle separation on the fan blades.
  • 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 from the impulse introduced by the additional blades on the particles, which has a component which is directed towards the carrier part.
  • a combination of different measures on the fan wheel for effecting a deflection of the particles towards the annular gap also makes sense.
  • Such a combination is particularly advantageous when a fan is combined according to claim 16 with a fan with the features of claim 12.
  • Such Fan wheel is particularly suitable for cleaning fluid that is loaded with a mix of particles of different sizes. Heavy particles are still promoted in the center of the radial impeller from the additional blades to the separation gap, while the smaller weight particles gradually over the strip-like projections on the working or pressure sides of the fan blades at the radial flow gradually towards carrier part and thus to the deposition Annular gap to be pushed.
  • the radial flow can be made even lossless, so that a further improvement of the efficiency can be achieved.
  • Fig. 1 is denoted by the reference numeral 12, the axis of a fan assembly, which is incorporated in a pipe section 60.
  • the pipe section 60 is part of a piping system for conveying fluid or fluid, which is loaded with particles to be separated in solid or liquid form.
  • an axially impinged radial impeller is installed in the pipe section 60, which is provided with the reference numeral 10.
  • This fan should be able to gaseous fluid containing abrasive particles, such as. As dust particles, water particles, snowflakes, fat particles and the like are loaded, effectively pumped or pumped from an environment.
  • the fan according to Fig. 1 also fulfills the task of largely separating these particles as they flow through the fan. For this purpose, the following structure is provided:
  • a designated 16 hub is non-rotatably mounted on a drive shaft of a motor 62 which is supported by a mounting plate 64.
  • the axis of the motor coincides with the axis 12.
  • the orientation of the axis is according to Fig. 1 vertical. However, it should be emphasized at this point that the axis can be equally horizontal without affecting the function of the fan with deposition.
  • the hub 16 further carries a blade support member 18 which extends substantially perpendicular to the axis of rotation 12.
  • the support member 18 carries a blade assembly having a plurality of annularly spaced circumferentially spaced apart and generally identically formed fan blades 20.
  • the fan 10 is thus flowing axially and has a blade assembly with which the substantially axially directed inlet SE is deflected radially outward ,
  • the blades have entry edges or leading edges 24, and radially outer exit edges 26.
  • Between the fan blades 20 substantially radially outwardly directed flow channels 28 are defined so that thus an axial inlet flow with rotating impeller 10 radially outward into an outlet flow SA with radial and directed in the circumferential direction velocity component is deflected.
  • the leading edges 24 and the flow exit edges 26 are associated with pitch circles, the pitch circle of the flow exit edges being designated 26a.
  • the diameter of the pitch circle 26a for the exit edges 26 is smaller, preferably considerably smaller, than the inner diameter of the tube section 60.
  • the blades 20 of the blade assembly are designed and / or oriented so that in the fluid to be delivered particles in the direction of a circumferential gap 40 predetermined axial extent between the support member 18 and a collecting trough 66 surrounding the support member and the impeller are deflectable.
  • the collecting channel is part of the mounting plate 64 and firmly connected to it and go from it - as best of the Fig. 2 can be seen - tangentially more circumferentially spaced from each other particle discharge pipes 68, are discharged through the deposited particles.
  • the particle discharge pipes 68 are thus connected to the collecting trough 66 in such a way that the circumferential speed of the fan wheel 10 rotating in the running direction RL can be utilized to increase the velocity of the particle flow in the particle discharge pipes 68.
  • the particle discharge pipes 68 can be used simultaneously for fastening the mounting plate 64 in the pipe section 60.
  • spokes 70 may be provided, which also like the particle discharge pipes 68 in a uniform circumferential distance each other and are firmly connected to the pipe section 60. The spokes 70 thus optionally carry in cooperation with the particle discharge pipes 68, the unit of motor 62, mounting plate 64 and impeller 10th
  • the pitch circle diameter 26a of the exit edges 26 is about 50 to 60% of the inside diameter of the pipe section 60 so that sufficient radial clearance remains for the flow exiting the fan wheel 10 which continues to flow in the axial direction.
  • Reference numeral 30 denotes an inlet funnel, with which the axially arriving flow is introduced into the impeller or fan wheel 10 with little loss. Equally, the back of the inlet funnel can be used to eliminate dead space behind the inlet funnel so as to keep the fluid flow through the pipe section 60 as lossless as possible.
  • the particle discharge pipes 68 are guided with a first portion 68 A radially outward in the direction of the pipe wall of the pipe section 60. There, they pass over a curved section 68B into a substantially axially extending axial section 68C secured to the inner wall of the tubular section 60.
  • the inner diameter of the particle discharge tubes is substantially the same size as the cross section of the collecting channel 66, so that a loss-free flow for the flow of the particle fluid results. It has been found that, for example, when using a fan with an outer diameter of, for example, 400 mm and an inner diameter of the pipe section 60, for example, 630 mm readily succeed, the particles from the collecting channel in the particle discharge pipes 68 with flow rates up to 50 m / s dissipate.
  • the relatively high flow velocity in the particle discharge pipe 68 effectively entrains the particles from the gutter 72, so that the latter together with the main particle flow can be discharged via the flexible pipe (not shown) at the downstream end of the axial sections 68C.
  • grooves 72A, 72B offset by 180 ° from one another are used. However, several such arrangements may be used in staggered form. It is only important that the grooves 72 detect a sufficiently large boundary flow in the region of the inner wall of the pipe section 60, so that the transported by the centrifugal effect outward particles that have missed the gap 40 between impeller or fan and collecting trough 66, effectively collected and can be separated.
  • the pitch angle of the grooves 72A, 72B can be varied within wide limits, it is preferably in the range between 5 ° and 35 °.
  • the blades 20 of the fan 10 are equipped with additional strips 48 a, 48 b, which ensure that the particles are pushed in the direction of annular gap 40 upon rotation of the fan.
  • additional strips 48 a, 48 b which ensure that the particles are pushed in the direction of annular gap 40 upon rotation of the fan.
  • FIGS. 7 and 8th a variant of a fan wheel is shown, which can be used in the inventive arrangement.
  • similar reference numerals are selected, but preceded by a "1".
  • the fan wheel which serves to convey a fluid, in particular a fluid laden with solid or liquid particles, is designated by the reference numeral 110.
  • the fan 110 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 110 has a rotation axis 112, which - as can be seen from the FIGS. 7 and 8th Detects - is vertically aligned. However, the orientation of the axis 112 is arbitrary. A designated 114 housing is not required.
  • a hub designated 116 is non-rotatably mounted on a drive shaft 113 of the motor, not shown, and it carries a blade support member 118 which extends substantially perpendicular to the axis of rotation 112.
  • the carrier part 118 in turn, carries a blade arrangement with a large number of fan blades 120 which are arranged in the manner of a circle at a circumferential distance from one another and are generally of identical design.
  • the Lüfterradschaufeln 120 are - as is apparent from the illustrations of FIGS. 9 and 10 results, to which extent already taken so far - to an axis 112 containing the axis of rotation 112, such as the plane of the Fig. 8 at a certain angle DELTA, so that they produce a radially outward flow when turning the fan 110 with the direction of rotation V.
  • the angle DELTA can also be 0 °.
  • the fan blades - as is apparent from the Fig. 8A results - are not aligned parallel to the axis of rotation 112, but they are to a normal plane 115, which coincides in the embodiment shown with the plane of the support member 118, at an angle WS ⁇ 90 °, that is employed 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.
  • FIGS. 7 to 8A are the fan blades 120 straight, resulting from the Fig. 7 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 fan blades 120 each have a radially inner leading edge 124 and a radially outer trailing edge 126. Between the fan blades 120 substantially radially outwardly directed flow channels 128 are defined so that thus an axial inlet flow - indicated by the arrow SE - with rotating fan 110th radially outward into an outlet flow SA with radial and directed in the circumferential direction velocity component is deflected.
  • leading edges 124 and flow exit edges 126 are each associated with a pitch circle 124a or 126a.
  • the flow entry edges 124 extend from a portion of the support member 118 near the hub 116 and extend axially therefrom to a blade edge 129 substantially parallel to the support member 118 (see FIGS Fig. 7 ).
  • the blades 120 end just below a top wall 117 of a housing.
  • the slightly modified variant according to Fig. 8 carry the blades on the support member 118 side facing away from an annular disk 121 and they are firmly connected to this, for example, welded.
  • the shape of the Lüfterradschaufeln 120 may - depending on the fan design - vary within wide limits. If the fan blades 120 - as in Fig. 8 4, the construction of the fan wheel becomes stiffer, so that it is sufficient to fix the fan blades to the carrier part 118, such as welding. The leading edge 124 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. 7 the advantage that fewer particles accumulate in the fan.
  • the flow entry edges 124 of the fan blades 120 are in the various sectional views perpendicular to the axis of rotation 112 on pitch circles 124a, which are part of a part of a circle, which a cylinder or truncated cone shell with a small cone angle WK (see Fig. 8 ) Are defined.
  • the fan 110 is installed in a housing 114, of which in the application for the present invention, only the collecting channel 142 and the inlet funnel or inlet nozzle 130 is required.
  • the collection trough 142 adheres to the radially outer blade edges 126 while maintaining a small gap 137.
  • the fan wheel 110 may also be provided with a bottom-side recess (not shown) into which the collecting channel 142 engages with a fit.
  • the upper edge 136 of the collecting channel 142 to a support member 118 closest to the edge 138 of the fan blades 120 axially spaced by a predetermined gap MS.
  • the upper edge 136 of the collecting channel 142 defines a radial or annular gap 140 for discharging particles separated from the fluid, such as dust, water, oil or grease particles.
  • the annular gap 140 is surrounded by the collecting channel 142.
  • the fan blades are aligned parallel to the axis of rotation 312, but they may also be inclined to the normal plane 315, which in the illustrated embodiment coincides with the plane of the beam 318, at an angle of attack ⁇ 90 °, i. be made such that 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 part.
  • the fan blades 320 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 flow-mechanical efficiency of the fan and / or the particle separation to be described later.
  • the Lüfterradschaufein 320 again each have a radially inner leading edge 324 and a radially outer trailing edge 326. Between the Lüfterradschaufeln 320 substantially radially outwardly directed flow channels 328 are defined, so that an axial inlet flow with rotating fan 310 radially outward into an outlet flow SA with radial and circumferentially directed velocity component is deflected.
  • leading edges 324 and flow outlet edges 326 are each assigned a pitch circle 324a or 326a.
  • the flow entry edges 324 extend from a portion of the support member 318 proximate to the hub 316 and extend axially therefrom to a blade edge 329 substantially parallel to the support member 318.
  • FIGS. 18 to 20 Carry the blades on the side facing away from the support member 318 side an annular disc 321 and they are firmly connected to this, for example, welded.
  • the axial extension H of the fan blades 320 thus determined as a distance between the support member 318 and the annular disc 321st
  • the flow entry edges 324 of the fan blades 320 are in the various sectional views perpendicular to the axis of rotation 312 on pitch circles 324a, which are part of a part of a circle, a cylinder or truncated cone shell with a small cone angle WK (see Fig. 20 ) Are defined.
  • the impeller is similarly installed in the pipe section as the fan wheels described above, so that a fluid-conveying function and in cooperation with the collecting trough and the particle discharge pipes, a particle-separating function is met.
  • additional axially projecting additional blades 344 are mounted radially inside the fan blades 320, wherein the axial extent of the additional blades is less than that of the fan blades 320.
  • the additional blades 344 are turned against the direction of rotation V, ie they close with the normal plane 315 to the axis of rotation 312 and with the plane of the support member 318 an angle WA> 90 °, thereby manages the wear of the fan blades 320 and optionally attached thereto strip-like projections, which in Fig. 18 indicated only by dashed lines and designated 348, to be evened.
  • the angle of attack WA can be up to 135 ° and is selected as a function of the particle size, load and consistency, and adjusted to the flow velocities in order to minimize the wear of the main blades.
  • the auxiliary blades 344 have an axial extent EA that is less than the height H of the fan blades 320.
  • the auxiliary blades 344 have a height EA which is up to 50%, preferably up to 30% of the axial extent H of the fan blades 320.
  • the fan blades 320 as well as the additional blades 344 made of sheet steel, wherein the material is tuned according to the ambient conditions in the use of the radial fan.
  • the material is tuned according to the ambient conditions in the use of the radial fan.
  • other materials can be used, depending on which properties are required in the long-term use.
  • Blades 320 and 344 are subject to different wear, so it is advantageous to keep the thickness D344 of the auxiliary blades larger than the thickness D320 of the main blades 320.
  • the thickness of the fan blades 320, 3120 and auxiliary blades 344, 3144 not to scale played. Contrary to the presentation in the FIGS. 19 and 20
  • the thickness D344 of the auxiliary blades 344 is about three times the thickness D320 of the fan blades. That is, with a thickness D320 of the fan blades 320 of, for example, 5 mm (which is realistic for a fan of up to 1000 mm diameter), the thickness D344 of the auxiliary blades is about 15 mm.
  • the additional blades 344 are offset to the fan blades 320 in the circumferential direction, in such a way that the deflected by the additional blades 344 particles under the influence of fluid mechanical and other dynamic forces do not hit the leading edges 324 of the fan blades 320 ,
  • the additional blades 344 may also overlap with the fan blades 320 in the radial direction.
  • each fan blade 320 can carry on its working or pressure side 346 at least one strip-like projection 348, which is employed to the flow direction in the flow channel 328 between the blades 320 such that the flow at least in Druckieridin axially on the support member 318th is deflected and the at a predetermined axial distance, which preferably not greater than the dimension MS - see Fig. 17 - Is, ends to the support member 318.
  • a strip-like projection 348 is provided at all, its height is kept rather small and should not exceed the dimension of 8 mm.
  • the particulate laden fluid preferably gaseous fluid, such as air
  • gaseous fluid such as air
  • the particulate laden fluid flows axially into the radial fan at 330. Due to the action of the fan blades 320 of the fan wheel 310 rotating at a predetermined speed, the flow is deflected into the channels 328 and conveyed radially outward. Due to the additional blades 344 according to the invention and their employment according to the invention at the angle WA> 90 °, the wear caused by the particles on the fan wheel 310 can be uniformed. In particular, the highly stressed blade roots 350 of the fan blades 320, but also the blade roots 352 of the auxiliary blades 344 can be effectively protected against excessive and rapid wear.
  • the fan blades 3120 are convex in the direction V.
  • the fan blades 3120 are smooth, resulting in good efficiency and low noise.
  • strip-like projections which terminate in a substantially identical axial distance MS from the carrier part 318 can also be provided on each fan blade.
  • the fan blades 320 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 the centrifugal and Coriolis forces are urged towards the support member 318, 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 flow layer pass through the annular gap 40 into the annular chamber 42, which is preferably designed so that no excessive back pressure is built up therein.
  • the main flow, which the fan 310 above the Ringspaces 40 leaves 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.
  • angle of attack WS of the fan blades 320, 3120 with respect to the normal plane 315 to the axis of rotation 312 can be varied in the radial direction, resulting in a kind of propeller shape for the blades.
  • the additional blades 3144 as well as the fan blades 3120 are convex. But they can also be straight or concave or S-shaped.
  • the strip-like projections 348a, 348b can also be given a different shape, for example be guided arcuately.
  • the invention thus provides an arrangement with a built-in a tube and in the axial direction promoting fan, which is driven by a motor.
  • the fan is formed by an axially impinged radial impeller with 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 exit edges of the blades of the fan are on a pitch circle, which is smaller than the inner diameter of the tube.
  • the blades of the blade arrangement are designed and / or aligned such that particles contained in the fluid to be conveyed are distractible in the direction of a circumferential gap of predetermined axial extent between the carrier part and a collecting channel surrounding the carrier part. From the collection trough, which is firmly connected to a mounting plate for the engine, go out tangentially a plurality of circumferentially spaced particle discharge pipes, which are preferably attached or welded to the inner wall of the tube.
EP08012256A 2008-07-07 2008-07-07 Ventilateur installé dans un tuyau Pending EP2143958A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP08012256A EP2143958A1 (fr) 2008-07-07 2008-07-07 Ventilateur installé dans un tuyau
CN200910211631A CN101699076A (zh) 2008-07-07 2009-07-07 安装在管中的风机

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP08012256A EP2143958A1 (fr) 2008-07-07 2008-07-07 Ventilateur installé dans un tuyau

Publications (1)

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EP2143958A1 true EP2143958A1 (fr) 2010-01-13

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EP08012256A Pending EP2143958A1 (fr) 2008-07-07 2008-07-07 Ventilateur installé dans un tuyau

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EP (1) EP2143958A1 (fr)
CN (1) CN101699076A (fr)

Cited By (6)

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WO2012080012A1 (fr) * 2010-12-14 2012-06-21 Voith Patent Gmbh Ventilateur radial doté d'une fonction de séparation des gouttes
EP2808553A3 (fr) * 2013-05-29 2014-12-10 Vorwerk & Co. Interholding GmbH Roue de ventilateur
DE102015213009A1 (de) * 2015-07-10 2017-01-12 Mahle International Gmbh Gebläseanordnung
DE102015213006A1 (de) * 2015-07-10 2017-01-12 Mahle International Gmbh Gebläseanordnung
DE102015122132A1 (de) * 2015-12-17 2017-06-22 Ebm-Papst Mulfingen Gmbh & Co. Kg Kantenberandung eines Rotationselements und Gebläserad
DE102022129601A1 (de) 2022-11-09 2024-05-16 Schweerbau International Gmbh & Co. Kg Absaugeinrichtung für Partikel bei der spanabhebenden Bearbeitung von Gleisschienen

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EP1961969A2 (fr) 2007-02-26 2008-08-27 Josip Pavetic Roue de ventilateur radiale
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DE941932C (de) * 1942-03-14 1956-04-19 Buettner Werke Ag Geblaeselaufrad fuer staubhaltige Gase
EP0615069A1 (fr) * 1993-03-09 1994-09-14 RATIONAL GmbH Roue de ventilateur
WO2004020837A1 (fr) * 2002-08-22 2004-03-11 Rational Ag Roue de ventilateur pourvue d'une separation de graisse integree et destinee notamment a un appareil de cuisson
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
DE10315341A1 (de) * 2003-04-03 2004-10-21 Mkn Maschinenfabrik Kurt Neubauer Gmbh & Co. Gargerät mit einem Gebläse mit Radialgebläserad und Abscheideelement
EP1961969A2 (fr) 2007-02-26 2008-08-27 Josip Pavetic Roue de ventilateur radiale
EP1961967A1 (fr) 2007-02-26 2008-08-27 Josip Pavetic Roue de ventilateur radial et ventilateur radial équipé de celle-ci
EP1961968A1 (fr) 2007-02-26 2008-08-27 Josip Pavetic Roue de ventilateur radial et ventilateur radial équipé de celle-ci doté d'une protection contre la fermeture

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WO2012080012A1 (fr) * 2010-12-14 2012-06-21 Voith Patent Gmbh Ventilateur radial doté d'une fonction de séparation des gouttes
EP2808553A3 (fr) * 2013-05-29 2014-12-10 Vorwerk & Co. Interholding GmbH Roue de ventilateur
DE102015213009A1 (de) * 2015-07-10 2017-01-12 Mahle International Gmbh Gebläseanordnung
DE102015213006A1 (de) * 2015-07-10 2017-01-12 Mahle International Gmbh Gebläseanordnung
DE102015122132A1 (de) * 2015-12-17 2017-06-22 Ebm-Papst Mulfingen Gmbh & Co. Kg Kantenberandung eines Rotationselements und Gebläserad
DE102022129601A1 (de) 2022-11-09 2024-05-16 Schweerbau International Gmbh & Co. Kg Absaugeinrichtung für Partikel bei der spanabhebenden Bearbeitung von Gleisschienen

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