EP2886874A1 - Roue radiale pour un ventilateur à tambour et ventilateur doté d'une telle roue radiale - Google Patents

Roue radiale pour un ventilateur à tambour et ventilateur doté d'une telle roue radiale Download PDF

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Publication number
EP2886874A1
EP2886874A1 EP14192425.8A EP14192425A EP2886874A1 EP 2886874 A1 EP2886874 A1 EP 2886874A1 EP 14192425 A EP14192425 A EP 14192425A EP 2886874 A1 EP2886874 A1 EP 2886874A1
Authority
EP
European Patent Office
Prior art keywords
radial impeller
impeller
cover
flow channel
radial
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Withdrawn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
EP14192425.8A
Other languages
German (de)
English (en)
Inventor
Daniel Gebert
Katrin Bohl
Erik Reichert
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.)
Ebm Papst Mulfingen GmbH and Co KG
Original Assignee
Ebm Papst Mulfingen GmbH and Co KG
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 Ebm Papst Mulfingen GmbH and Co KG filed Critical Ebm Papst Mulfingen GmbH and Co KG
Publication of EP2886874A1 publication Critical patent/EP2886874A1/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Withdrawn legal-status Critical Current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
    • F04D29/18—Rotors
    • F04D29/22—Rotors specially for centrifugal pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
    • F04D29/281—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for fans or blowers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
    • F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps
    • F04D29/667—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps by influencing the flow pattern, e.g. suppression of turbulence
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D17/08—Centrifugal pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
    • F04D29/281—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for fans or blowers
    • F04D29/282—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for fans or blowers the leading edge of each vane being substantially parallel to the rotation axis
    • 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
    • F04D29/30—Vanes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/4206—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps
    • F04D29/4226—Fan casings
    • F04D29/4233—Fan casings with volutes extending mainly in axial or radially inward direction
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
    • F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps
    • F04D29/666—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps by means of rotor construction or layout, e.g. unequal distribution of blades or vanes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
    • F04D29/68—Combating cavitation, whirls, noise, vibration or the like; Balancing by influencing boundary layers
    • F04D29/681—Combating cavitation, whirls, noise, vibration or the like; Balancing by influencing boundary layers especially adapted for elastic fluid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/4206—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps
    • F04D29/4226—Fan casings

Definitions

  • the present invention relates to a radial impeller with axial air inlet and air outlet over the impeller circumference, preferably for use in a spirally designed housing, with a bottom plate, which has an outside diameter, and with a concentric with the bottom plate axially spaced cover plate, which for the axial air inlet has a circular suction opening with an inner diameter, and with a plurality of arranged between the bottom plate and the cover disc, forward curved, profiled blades, wherein between each two adjacent blades a flow channel with a radially inner air inlet side and a radially outer Air outlet side is formed, seen in the direction of the radial impeller - convex curved.
  • This channel curvature means that the suction-side surfaces of the blades-at least in some regions-are convex and their pressure-side surfaces-at least in regions-are concavely curved.
  • the present invention relates to a fan unit, in particular a drum fan, with such a radial impeller.
  • fan here fans are subsumed with a pressure ratio between the suction and discharge side in the range of 1.0 to 1.1 and blowers with a pressure ratio between the intake and pressure side in the range 1.1 to 3.0.
  • radial impellers are preferably used where a high pressure build-up is to be achieved at a lower volume flow. With radial impellers, the entire flow of air delivered leaves the impeller at the outer diameter, it is possible to produce a higher kinetic energy of the air molecules and thus a higher pressure than an axial fan whose peripheral speed is limited at the wheel hub.
  • radial impellers are particularly effective when an air flow must be deflected by 90 ° from the axial in the radial direction, or if components, filters o. ⁇ . Impair a free air flow.
  • the most common design is as a one-piece radial all-in-one fan, although there are also different engine / impeller combinations for applications where the air duct can be integrated into a unit for pressure build-up.
  • impellers with forwardly curved blades in the running direction those with rearwardly curved blades and those with radially ending blades.
  • Forward - in the direction of rotation - curved blades cause the flow channel, which runs from a radially inner air inlet side to a radially outer air outlet side, - seen in the running direction of the radial impeller - is convexly curved.
  • the suction-side surfaces of the blades are thus - at least partially - convex and their pressure-side surfaces - at least partially - concave curved.
  • Radial impellers with forward curved blades allow a high swirl of the air flow and thus achieve a high energy conversion.
  • the disadvantage is a high dynamic pressure of the exiting air.
  • This dynamic pressure must be converted into static pressure in a downstream diffuser, such as a volute casing.
  • Radial impellers with forwardly curved vanes impart more swirl to the flow than radial impellers with backward-curved vanes.
  • the speed required to achieve the same operating point is with radial vanes with forward curved vanes as compared to radial vanes with backward curved vanes same size much lower.
  • the efficiency of radial impellers with backward curved blades is significantly higher than that of radial impellers with forward curved blades.
  • Drum fans are radial fans whose impellers are the same as a drum. H. the impeller width is relatively large compared to the wheel diameter. It may in particular be in the range between 40 and 80 percent, based on the outer diameter of the bottom disk.
  • Scirocco runners for about 80 years, provided with forward curved blades runners are used in applications that require small radial dimensions.
  • the ratio of the inner diameter of the cover disc to the outer diameter of the bottom disc of the original Scirocco rotor was 0.875.
  • Drum roller fans are used in the field of air conditioning and air conditioning in systems with a required pressure increase of preferably up to 4000 Pa and with flow rates up to 8 m 3 / s - related to a wheel diameter of one meter and a single-flow design.
  • the thickness of the blades is variable over their Wareckungsraum, in particular, the blades then profiled as strong be regarded, if in them a so-called profile thickness ratio, ie a ratio of profile thickness to total profile length, greater than or equal to 0.15, in particular greater than or equal to 0.2 and particularly preferably greater than or equal to 0.25.
  • the profile thickness ratio is at most preferably 0.5, in particular 0.4 and particularly preferably 0.35.
  • cover plate is referred to there as a frame and is part of the spiral housing.
  • a detachment on the cover plate is disadvantageously reinforced by the known blade profiling. An increase in the efficiency is thus possible by this measure only to a very limited extent.
  • the present invention is based on the object to provide a radial impeller of the type mentioned and a fan unit with such a radial impeller in which unite the advantages of a drum rotor with those of an impeller with backward curved blades, with which in particular an increase in efficiency while maintaining a high power density and low noise can be achieved.
  • this is achieved in that the outer diameter of the bottom disc of the radial impeller - based on the inner diameter of the suction port - at least 20% larger than the inner diameter of the suction port, that the cover disc forms a deck-side guide surface in the flow channel, wherein a in the direction the inlet opening angle, which is formed between a tangent to the deck-side guide surface at the entrance to the suction port of the cover plate and a tangent to the deck-side guide surface at the exit from the flow channel at its radially outer air outlet side is at least 30 °.
  • a fan unit according to the invention is characterized in that the radial impeller according to the invention is arranged in a housing, in particular in a spiral-shaped housing.
  • drum rotor radial impellers By the invention, the advantage of previously known as drum rotor radial impellers can be maintained that they have a high power density and a low noise with low rotary sound overshoot compared to radial impellers with backward curved blades.
  • the advantageously high power density is attributable to a high swirl supply of the flow through the forward curvature of the blades.
  • a low noise is promoted by preferably high numbers of blades and preferably low speeds during operation.
  • Both the forward curvature, and in particular a high Schaufelan endeavor prevent or at least reduce detachment of the blades and the cover plate, but increase the frictional forces, which can lead to losses and a reduction in efficiency.
  • the inventive geometric design of the radial impeller which can be provided in a preferred embodiment, that the outer diameter of the bottom plate - based on the inner diameter of the intake of the cover plate - 50% larger, at most by more than 90% larger than the inner diameter of the cover plate is.
  • CFD computational Fucid D ynamics
  • a detachment of the cover plate which can be detected by a so-called CFD flow simulation.
  • CFD computational Fucid D ynamics
  • the Navier-Stokes equations used in fluid mechanics and describing momentum and mass conservation are modeled mathematically under specification of certain boundary conditions. This represents a cost-effective alternative to elaborate, for example in wind tunnel experimental series of experiments and makes it possible to analyze flow parameters, the can not be detected metrologically, such as turbulent kinetic energy, turbulence viscosity, etc.
  • cover plate To prevent detachment of the cover plate also contributes to a design of the cover plate with preferably relatively large axial width, after which the width of the cover plate can preferably occupy at least 30% of the total width of the impeller.
  • a width dimensioning is considered to be synergistically effective in combination with the invention, since in conventional drum travelers with unprofiled blades no improvement can be achieved by this design.
  • the efficiency is determined by the volume flow and by the total pressure increase caused by the fan, from the product of which the flow rate results, according to the so-called Bernoulli equation under total pressure the sum of static and dynamic pressure is understood.
  • a further increase in efficiency of a total blower with the radial impeller according to the invention can be achieved by selecting a width ratio of a housing width at the impeller outlet to impeller outlet width itself of at least 1.0 up to a maximum of 1.4.
  • ⁇ r is the delivery number, where the index r stands for "radial"
  • V is again the volume flow in m 3 / s
  • D is the impeller outer diameter in m, which is determined by the outlet diameter D a, S of the blades, b the outlet width of the impeller in m and n the speed in 1 / min.
  • the inventive design of the cover additionally optionally advantageously also a nozzle-shaped design of the inlet and an axial immersion of the nozzle be provided in the cover plate.
  • the split flow can be directed in the same direction as the main volume flow entering through the suction port.
  • the split flow then advantageously contributes to the stabilization of the deflection in the radial direction, as is known to occur only with radial wheels with backward curved blades.
  • the radial impeller is characterized in that the number of blades is at least 19 and at most 54, and preferably in the range of 22 to 46.
  • the radial impeller is further characterized in that in each case the leading edges of the blades are rounded at the radially inner air inlet side and / or the trailing edges of the blades at the radially outer air outlet side.
  • the fan unit is characterized in one embodiment in that the housing has a spirally wound around the radial impeller air duct with an oval, from the side of the radial impeller forth steadily increasing cross section.
  • a radial impeller 10 has a cover disk 1, a plurality of forwardly curved, profiled blades 2 and a bottom disk 3.
  • the cover plate 1 forms a suction mouth and thus has a circular intake opening 4 with an inner diameter D i, DS for an axial air inlet.
  • the bottom plate 3 has an outside diameter D a, BS and is arranged concentrically with the cover plate 1 axially spaced from the cover plate 1.
  • the blades 2 are located between the cover plate 1 and the bottom plate 3. Between each two blades 2, a flow channel 5 is formed, which-seen in the direction LR of the radial impeller 10 - is convexly curved, and in which the flow in a direction S from a radially inner air inlet side 5a to a radially outer air outlet side 5b takes place.
  • the at least partially convex curvature of the flow channel 5 - seen in the direction LR of the radial impeller 10 - means that, as Fig.
  • FIG. 2 shows a pressure side 2c of the blade 2, which - seen in the direction LR of the radial impeller 10 - each under the blade 2, at least partially concave, and a suction side 2d of the blade 2, which - seen in the direction LR of the radial impeller 10 - in each case lies on the blade 2, at least partially convexly curved.
  • the cover plate 1, the blades 2 and the bottom plate 3 may preferably be designed as a composite of two parts, in particular of two injection molded plastic parts, materially connected composite body.
  • Profiling of the blades 2 means that the profile thickness d S of the blade 2 is not constant over its length.
  • Characteristic of the profiling of the blades 2 is a profile thickness ratio, which by the ratio V P of maximum profile thickness d S to the profile total length L S (see Fig. 2 ) and should be at least 0.15, in particular at least 0.2 and particularly preferably at least 0.25, wherein the profile thickness ratio V P can be at most 0.5, in particular 0.4 and particularly preferably 0.35.
  • the position of the maximum profile thickness d S can preferably be in the range of 5% to 75% of the overall profile length L S - seen from the air inlet side 5 a - and reduces from there, both in the direction of the front edge 2 a of the blade 2, as also towards the trailing edge 2b.
  • each of the leading edges 2a and / or the trailing edges 2b of the blades 2 are rounded.
  • the blade shape optional or preferably descriptive features are a crescent-shaped, but asymmetrical cross section of the blades 2, an at least partially convex outer curvature of the suction side 2d, which is greater than the at least partially concave inner curvature of the pressure side 2c, and a teardrop shape with respect to the curved center axis through the blade 2.
  • An optimum number of blades 2 is at least 19 and at most 54, and is preferably in the range from 22 to 46, in a characteristic manner for a drum fan. High numbers of blades can cause obstruction of the flow channel 5 and reduce the maximum possible volume flow V. Also, the friction losses on the blade walls may increase, so that there is a decrease in the efficiency ⁇ .
  • a radial impeller 10 according to the invention is preferably intended for use in a fan unit 20 according to the invention.
  • the radial impeller 10 according to the invention may preferably be arranged coaxially to an electric drive motor 6 and is located in a housing 7, in which it - as in Fig. 3 shown - may preferably act around a spiral-shaped housing 7.
  • the fan unit 20 is a fan with a forwardly curved radial wheel. It can preferably be a drum fan, for which it is also characteristic that the total width b tot of the radial impeller 10 is in the range from 25% to 70% of the outside diameter D a, BS of the bottom disk 3. As Fig. 1 shows, this results in the total width b ges as Sum of a width b DS of the cover plate 1 and an impeller outlet width b 2 on the radially outer air outlet side 5b of the flow channel fifth
  • the outer diameter D a, BS of the bottom plate 3 - based on the inner diameter D i, DS of the cover plate 1 - at least 20%, preferably by at least 50%, greater than the inner diameter D i, DS of the cover plate. 1 is.
  • the cover plate 1 forms for the flow channel 5, a deck-side guide surface 8, wherein an opening in the direction of the inlet 4 opening angle ⁇ DS , between a tangent T 1 to the deck-side guide surface 8 at the inlet into the intake 4 of the cover plate 1 and a Tangent T 2 is formed on the cover-side guide surface 8 at the exit from the flow channel 5 at its radially outer air outlet side 5b, is at least 30 °.
  • the maximum value of this angle can be at 90 °, preferably at 75 °.
  • the tangent T 1 runs in the first embodiment parallel to the longitudinal axis XX of the radial impeller 1. In this way, according to the invention such aerodynamically favorable flow deflection from the axial in a radial or diagonal direction that while maintaining the advantages of conventional drum runners to a Increase in the efficiency ⁇ comes.
  • the bottom plate 3 in the flow channel 5 can form a bottom-side guide surface 9 in the flow channel 5.
  • the cover-side guide surface 8 and / or the bottom-side guide surface 9 of the flow channel 5 can in particular, as in the drawing - except for the bottom plate 3 of the embodiment in Fig. 4 - Shown to be executed curvature continuous, which counteracts the advantage of the formation of flow turbulence.
  • a respective shortest, preferably between air inlet side 5a and air outlet side 5b of the flow channel 5 variable distance between bottom plate 3 and cover plate 1 is located.
  • A can be advantageously provided that it decreases in the direction S from the radially inner air inlet side 5a to the radially outer air outlet side 5b, in particular taking into account the determined by the number of blades 2 blade spacing such that the cross-section the respective flow channel 5 tapers.
  • an inlet 21 of the housing 7 is designed nozzle-shaped for the radial impeller 10, wherein the inlet 21 of the housing 7 is immersed in particular in the suction port 4 of the cover plate 1, as most clearly Fig. 3 , but also Fig. 4 and 5 demonstrate.
  • the nozzles do not submerge in the cover disk.
  • the static pressure difference at a gap between the nozzle-shaped inlet and the cover plate is too low in known radial wheels with forward curved blades, to achieve that axially through the inlet - along the longitudinal axis XX - moving main flow by a pulse supply from the additionally by the gap flows laterally into the intake opening of the cover disk reaching gap flow to the cover disk.
  • the blades are thereby flowed axially near the cover disk, whereby the flow already separates at the blade entry edges.
  • the immersion length L E of the gap 22 may be a size in the range of 0.5% to 5.0%, preferably in the range of 1.0% to 3.0%, of the outer diameter D a, DS of the cover plate 1 and a gap width S W of the gap 22 have a size in the range of 0.5% to 5.0%, preferably 1.0% to 3.0%, of the outer diameter D a, DS of the cover plate 1 have.
  • a ratio V B of a width B of the housing 7 at its air inlet opening 7b in the air duct 7a to a impeller outlet width b 2 of the radial impeller 10 at the radially outer air outlet side 5b of the flow channel 5 has a value which in the range 1.0 ⁇ V B ⁇ 1.4.
  • the housing 7 has a spiral air duct 7a spirally wound around the radial impeller 10 - not with a rectangular but with an oval, preferably elliptical, side of the radial impeller 10 has continuously increasing cross-section.
  • the ratio of the major to the minor axis of the ellipse may preferably be in the range of 1.2 to 3.0, wherein the major axis is different -.
  • B preferably vertically or horizontally - may be oriented.
  • an outlet diameter D a, S of the blades 2 on the cover plate 1 is smaller than or equal to the outer diameter D a, DS of the cover plate 1. It can also be provided that this outlet diameter D a, S is less than or equal to the outer diameter D a, BS of the bottom plate 3.
  • cover-side guide surface 8 and / or the bottom-side guide surface 9 of the flow channel 5 has already been stated that they can be performed curvature continuous.
  • cover-side guide surface 8 and / or the bottom-side guide surface 9 of the flow channel 5 has already been stated that they can be performed curvature continuous.
  • a double-flow design of the radial impeller 10 according to the invention is possible without departing from the scope of the invention.
  • the invention has hitherto not been limited to the feature combinations defined in the independent claims 1 and 15, but may also be defined by any other combination of certain features of all the individual features disclosed overall. This means that in principle virtually every individual feature of the independent claims can be omitted or replaced by at least one individual feature disclosed elsewhere in the application.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
EP14192425.8A 2013-12-20 2014-11-10 Roue radiale pour un ventilateur à tambour et ventilateur doté d'une telle roue radiale Withdrawn EP2886874A1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102013114609.0A DE102013114609A1 (de) 2013-12-20 2013-12-20 Radial-Laufrad für einen Trommellüfter und Lüftereinheit mit einem derartigen Radial-Laufrad

Publications (1)

Publication Number Publication Date
EP2886874A1 true EP2886874A1 (fr) 2015-06-24

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP14192425.8A Withdrawn EP2886874A1 (fr) 2013-12-20 2014-11-10 Roue radiale pour un ventilateur à tambour et ventilateur doté d'une telle roue radiale

Country Status (4)

Country Link
US (1) US20150176594A1 (fr)
EP (1) EP2886874A1 (fr)
CN (2) CN104728160B (fr)
DE (1) DE102013114609A1 (fr)

Cited By (1)

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Publication number Priority date Publication date Assignee Title
IT201800003845A1 (it) * 2018-03-21 2019-09-21 Almes S R L Dispositivo di ventilazione per elettrodomestici

Families Citing this family (13)

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Publication number Priority date Publication date Assignee Title
DE102013114609A1 (de) * 2013-12-20 2015-06-25 Ebm-Papst Mulfingen Gmbh & Co. Kg Radial-Laufrad für einen Trommellüfter und Lüftereinheit mit einem derartigen Radial-Laufrad
JP6438860B2 (ja) * 2015-07-31 2018-12-19 ミネベアミツミ株式会社 遠心ファン
ITUB20152807A1 (it) * 2015-08-03 2017-02-03 Ma Ti Ka S R L Ventola per forni per la cottura di alimenti
CN105387003B (zh) * 2015-12-16 2018-11-02 珠海格力电器股份有限公司 一种风机导流装置及离心风机
US20180023587A1 (en) * 2016-07-19 2018-01-25 Minebea Mitsumi Inc. Centrifugal Fan
EP3580462B1 (fr) * 2017-02-10 2021-12-22 Sew-Eurodrive GmbH & Co. KG Ensemble de ventilateur à ventilateur et bague dentée et moteur à convertisseur comprenant l'ensemble de ventilateur
EP3460256A1 (fr) 2017-09-20 2019-03-27 Siemens Aktiengesellschaft Dispositif pouvant être traversé
WO2019115717A1 (fr) * 2017-12-13 2019-06-20 Ebm-Papst Mulfingen Gmbh & Co. Kg Boîtier fabriqué en une seule opération
JP7467025B2 (ja) * 2018-03-26 2024-04-15 東芝キヤリア株式会社 送風機および空気調和機の室内ユニット
GB2585707B (en) * 2019-07-15 2021-08-11 Dyson Technology Ltd Variable radial inlet guide vane assembly
JP7348500B2 (ja) * 2019-09-30 2023-09-21 ダイキン工業株式会社 ターボファン
CN113153811B (zh) * 2021-05-30 2022-05-27 台州学院 一种采用轴盘降低静压损失的无蜗壳离心通风机
CN116201763B (zh) * 2023-01-16 2023-09-26 威海克莱特菲尔风机股份有限公司 一种低比转速小机壳离心风机的前向异型叶轮

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CN104728160A (zh) 2015-06-24
CN104728160B (zh) 2017-07-11
CN204646777U (zh) 2015-09-16
DE102013114609A1 (de) 2015-06-25

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