EP0112932B1 - Ventilateur radial avec des aubes profilées courbées en arrière - Google Patents

Ventilateur radial avec des aubes profilées courbées en arrière Download PDF

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Publication number
EP0112932B1
EP0112932B1 EP82112081A EP82112081A EP0112932B1 EP 0112932 B1 EP0112932 B1 EP 0112932B1 EP 82112081 A EP82112081 A EP 82112081A EP 82112081 A EP82112081 A EP 82112081A EP 0112932 B1 EP0112932 B1 EP 0112932B1
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EP
European Patent Office
Prior art keywords
blade
radial
radial fan
fan according
blades
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.)
Expired
Application number
EP82112081A
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German (de)
English (en)
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EP0112932A1 (fr
Inventor
Fritz Köger
Udo Haas
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.)
Cambio Sede masco GmbH
Original Assignee
Wilhelm Gebhardt GmbH
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 Wilhelm Gebhardt GmbH filed Critical Wilhelm Gebhardt GmbH
Priority to DE8282112081T priority Critical patent/DE3264089D1/de
Priority to EP82112081A priority patent/EP0112932B1/fr
Priority to AT82112081T priority patent/ATE13711T1/de
Priority to US06/565,656 priority patent/US4526506A/en
Publication of EP0112932A1 publication Critical patent/EP0112932A1/fr
Application granted granted Critical
Publication of EP0112932B1 publication Critical patent/EP0112932B1/fr
Expired 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
    • F04D29/30—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
    • F04D29/26—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
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2250/00—Geometry
    • F05D2250/70—Shape

Definitions

  • the invention relates to a radial fan according to the preamble of claim 1.
  • centrifugal fan which is known in practice, is the result of a development which has set itself the goal of developing radial fans with backward-curved blades to the highest power densities, while at the same time ensuring good efficiency and an overload-proof performance characteristic.
  • the description of the centrifugal fan is used in the following, as usual, dimensionless characteristic numbers which take into account the known dependencies of the volume flow V and the pressure increase ap t on the diameter D and the number of revolutions n of the impeller and the density p of the medium to be conveyed. The too defined volume number and the pressure number eliminate these dependencies and allow a direct comparison of centrifugal fans of different sizes and sizes.
  • a centrifugal fan is characterized by a characteristic curve that shows ⁇ t as a function of ⁇ .
  • Optimal operating conditions are achieved at an optimum point characterized by the pair of values ⁇ t ,, ⁇ opt , in which the efficiency ⁇ of the radial fan has its maximum ⁇ max .
  • This high power density which approximates that of a drum rotor fan with forward-curved blades, characterizes an already very compact centrifugal fan.
  • it allows a fan with the same size of the volute casing and the same impeller diameter to be optionally equipped with a rotor with backward curved blades or a drum rotor.
  • This enables standardization and large-scale production, which has major advantages, particularly in ventilation and air conditioning unit construction.
  • the object of the invention is to further improve a radial fan of the type mentioned while maintaining the success achieved.
  • the power density at the optimum point should be increased to a value above 0.2, the number of volumes not less than 0.2 and the efficiency should be 80% and more.
  • These requirements correspond to an even more compact design of the centrifugal fan with constant or decreasing energy requirements, which also meets the highest demands for energy saving and economic efficiency of systems.
  • deviations in the volume number ⁇ from ⁇ opt should go hand in hand with the smallest possible changes in the efficiency ⁇ .
  • the aim is to minimize the efficiency ⁇ in an operating range around ⁇ opt .
  • the invention is intended to expand the volume number range, in which ⁇ is at least 80%.
  • This requirement corresponds to the possibility of operating the centrifugal fan according to the invention with high efficiency even at operating points of its ⁇ - ⁇ t characteristic which are off the optimum point. This simplifies the selection of fans for equipping a given system and keeps the number of types required to cover the operating conditions that occur low.
  • Blade inlet angle and blade outlet angle should be larger on the cover disc side than on the trash disc side.
  • curved blades are also described in DE-AS-1 057 725, which also discloses the possibility of an inverted curvature and a streamlined profile.
  • DE-AS-1 057 725 which also discloses the possibility of an inverted curvature and a streamlined profile.
  • the radial fan according to the invention has a spiral housing 1, in which a radial impeller 2 is installed.
  • the radial impeller 2 is rotatably mounted on a shaft 3. It is set in rotation in the direction of arrow 4 by a drive unit (not shown). This will in the axial direction, d. H. in the axial direction of the shaft 3, a medium to be conveyed is sucked into the spiral housing 1 and ejected in the radial direction. The medium enters the interior of the volute casing 1 through an inflow nozzle 5.
  • the inflow nozzle 5 is arranged on the side of the spiral housing 1, specifically in the form of a collar which overlaps the edge of an inflow opening 6 and tapers inwards in the shape of a funnel.
  • the inner edge 7 of the inflow nozzle 5 forms an approximately cylindrical sleeve with which the inflow nozzle 5 engages over a cover plate 8 delimiting the radial impeller 2.
  • the inflow nozzle 5 comes to lie radially within the cover plate 8.
  • a gap 10 remains between the inflow nozzle 5 and the section 9 of the cover plate 8 overlapping it. Starting from the overlapping section 9, the cover plate 8 runs radially outward in the form of a curved deflection contour 11.
  • the deflection contour 11 terminates with the top 12 of a number of blades 13, which are mounted with their bottom 14 on a support plate 15 of the radial impeller 2.
  • the blades 13 have a backward curved, profiled contour, which will be explained in more detail below.
  • FIG. 2 a two-sided suction arrangement of the radial fan according to the invention is shown, which finds a preferred embodiment for air conditioners and air conditioners.
  • the radial fan is constructed symmetrically to a central plane in which the support plate 15 of the radial impeller 2 is arranged.
  • the support plate 15 is equipped on both sides with blades 13, which are covered on their top 12 by a cover plate 8 each.
  • Each of the cover plates 8 overlaps the inflow nozzle assigned to it with a rounded deflection contour 11, with an intermediate space each remaining in the form of the gap 10.
  • Each of the half sides of the radial impeller 2 on both sides of the support plate 15 thus exerts a suction effect in the axial direction, by means of which opposing media flows are conveyed through the side walls 17, 18 into the radial fan.
  • the media flows are ejected in the radial direction into a common spiral housing 1, which they leave through an exit surface 16.
  • the half sides of the radial impeller 2 are completely symmetrical; Dimensions that are shown in FIG. 2 on one half of the radial fan therefore also apply accordingly to the other half.
  • the contour of the blades 13 on both half sides of the radial impeller 2 is the same.
  • the contour of the blades 13 will now be described below. 2, it can first be seen that the blade inner diameter, ie the diameter of a circle described about the impeller axis and touching the inner edges 19 of the blades 13, decreases from the cover plate 8 to the support plate 15.
  • the blade inner diameter has a maximum value d 1max on the cover plate 8.
  • the average blade inner diameter d results from this
  • the inner edges 19 of the blades 13 lie on a surface of revolution around the axis of rotation of the radial impeller 2, which tapers in a funnel shape from the cover plate 8 to the support plate 15.
  • the surface of revolution that grips the outer edges 20 of the blades is cylindrical.
  • the outer contour of the blades 13 can thus be described over the full height between the cover plate 8 and the support plate 15 by an approximately constant blade outer diameter d 2 .
  • the blades 13 are twisted in themselves, so that the blade inner edges 19 and the blade outer edges 20 are each skewed on the rotating surfaces enveloping them, ie do not come to lie parallel to the axis of rotation of the radial impeller 2.
  • the view of the blade 13 in FIG. 3 is directed downwards onto the support plate 15 as in FIG. 1.
  • the cover plate 8 coming into contact with the top 12 of the blade 13 is removed.
  • the blade 13 is mounted on the support plate 15 with the partially concealed underside 14. Due to the twisting of the blade 13, a change in the blade entry angle ⁇ 1 and the blade exit angle ⁇ 2 is achieved via the height of the radial impeller 2.
  • the blade entry angle ⁇ is parallel to the support plate 15 in planes Are defined.
  • the blade exit angle ⁇ 2 is also defined in the same planes parallel to the support plate 15. It is enclosed in each case by a profile center line 24 of the blade 13 on the one hand and a tangent 26 placed on the rotational surface formed by the blade outer edges 20 on the other hand.
  • Fig. 3 further shows that the blade 13 is profiled in a particularly favorable form in terms of flow technology.
  • the design of the profile is particularly evident on the top side 12 of the cover plate and the underside 14 of the blade 13 on the support plate side.
  • It is an aircraft wing profile as used for low airspeeds, ie airspeeds up to approximately 250 km / h.
  • the blade 13 has such a profile over its full height, ie the entire area between the cover plate 8 and the support plate 15.
  • Each cut to the support plate 15 thus shows by a blade 13 in a plane parallel as a sectional area an aircraft Tragfläc h s p rofile of the type specified.
  • the profile of the blade 13 is, relative to the direction of rotation of the radial impeller 2 is curved rearward.
  • the blade exit angle ⁇ 2 therefore takes on values of less than 90 ° throughout.
  • the profile is twisted in the manner shown.
  • the desired high power density of the centrifugal fan is achieved in that with a ratio of the average blade inner diameter d 7 to the blade outer diameter d 2 - of approximately 0.7: 1, the blades 13, which are shaped in the form of an aircraft wing profile, are formed in this way are that the shovel entry angle ß 1 D on the cover plate side is 4 ° to 7 ° smaller than the shovel entry angle ß 1 T on the support plate side, and likewise the shovel exit angle ⁇ 2 D on the cover plate side is 3 ° to 6 ° smaller than the support plate side Blade exit angle ⁇ 2 T , the cover plate-side blade entry angle ⁇ 1 D between 14 ° and 20 ° and the cover plate-side blade exit angle ⁇ 2 D between 39 0 and 45 °.
  • Extensive tests have shown that with a dimensioning in the specified range, optimal operating data for a radial fan can be achieved.
  • the specified angular relationships can be achieved, inter alia, by twisting the blades 13.
  • the shovel entry angle ß 1 D on the cover plate side is 14.5 ° to 17.5 ° and the shovel entry angle ß 1 T 21.5 ° on the support plate side, while the shovel exit angle ß 2 D is 40 ° to 43 ° on the cover plate side and the blade-side blade exit angle ⁇ 2 T is 46 °.
  • the blade shape shown in FIG. 3 is created by twisting about a twist axis 22 running perpendicular to the plane of the drawing.
  • the twist axis 22 is thus oriented parallel to the axis of rotation of the radial impeller 2. It lies in a central area of the blades 13.
  • FIG. 4 Such an alternative arrangement is shown in FIG. 4.
  • the viewing direction is the same as in Fig. 3, and matching parts are provided with the same reference numerals.
  • the illustrated blade 13 is profiled and curved backwards.
  • FIG. 5 shows a further, alternative exemplary embodiment of a twisted blade 13.
  • the twist axis 22, which is oriented parallel to the axis of rotation of the radial impeller 2 is again laid in the central region of the blade 13.
  • the blade inner edge 19 is inclined in such a way that the rotary surface enveloping all the blade inner edges 19 forms a cone tapering from the cover plate 8 to the support plate 15.
  • the blade inner diameter is thus greater at the height of the cover plate 8 than at the height of the support plate 15.
  • the blade outer edge 20 of the blades 13 now experiences a similar inclination due to the twisting around the torsion point 22.
  • the rotating surface enveloping all the blade outer edges 20 has the shape of a conical jacket that widens from the cover plate 8 to the support plate 15.
  • the blade outer edge 20 is not approximated by a single one over the height of the blade 13 constant blade outer diameter d 2 described. Rather, the blade outer diameter varies over the height of the blade 13, whereby it its minimum Shall d 2min in height of the cover plate 8, and its maximum value d 2max at the height of the support plate 15 occupies.
  • An average blade outer diameter d 2 is to be set for the ratio of blade inner diameter to blade outer diameter specified in claim 1. As is easy to be convinced, the angular relationships given are also present in this arrangement, so that the teaching of the invention can be implemented.
  • FIG. 6 shows a further, alternative blade shape, which is not produced by twisting the blade profile but by shearing transversely to the longitudinal direction of the blade 13. Because of this shearing, the blade 13 is inclined from the cover plate 8 to the support plate 15 against the direction of rotation of the radial impeller 2.
  • the blade outer edges 20 have an approximately constant diameter d 2 over the height of the blades 13.
  • the blade inner edges 19 are inclined in a way by the shear. that its envelope forms a funnel-shaped surface of revolution tapering from the cover plate 8 to the support plate 15.
  • the blade 13 thus has on its inner edge 19 at the height of the cover plate 8 a larger inner diameter than in the region of the support plate 15.
  • the arrangement according to the invention can be characterized in that the profile chords of the blade cuts lie in different planes along the blade width measured perpendicular to the main flow direction.
  • the invention provides a radial fan whose power density, ie the product of ⁇ opt and ⁇ t , with a volume numberharide opt of 0.2 and more is greater than 0.2 and thus higher than in all radial fans that have been disclosed to date.
  • the volume number range ⁇ ⁇ 0.8 in which the radial fan operates with an efficiency ⁇ of more than 80%, was increased on both sides by at least 20% compared to the prior art.
  • FIG. 7 The diagram of the efficiency ⁇ over ⁇ is also plotted in this diagram with a separate scale.
  • the efficiency ⁇ takes its maximum value ⁇ max at a volume number ⁇ opt of over 0.2.
  • the associated value ⁇ topt is 0.94, so that the power density as a product of ⁇ opt and ⁇ topt is above 0.2.
  • the efficiency ⁇ on both sides of its maximum value ⁇ max decreases only very gradually compared to increasing or decreasing volume numbers ⁇ .
  • a blade cut can thus be selected in which the sides forming the blade outer edges 20 run at right angles to the sides which delimit the underside 14 of the blade 13 which comes into contact with the support plate 15.
  • Such a blade cut is particularly favorable in terms of production technology, since it results in low waste and simple processing.
  • An essential parameter for the invention is the inlet diameter d o of the cover plate 8, ie the smallest diameter of its pouring area.
  • the inlet diameter d o is shown in Figure 2. According to the invention, it should be about 0.75: 1 for the blade outer diameter d 2 .
  • the design of the deflection contour 11 of the cover plate 8 is also functionally important for the radial fan according to the invention. This is in the form of a cone cut, ie. H. circular, parabolic or hyperbolic curved and is therefore described by one or more radii of curvature r.
  • Figure 2 shows a circular curvature of the deflection contour 11 with a single radius of curvature r.
  • the radius of curvature (s) r for the inlet diameter d o must be 0.2 to 0.3: 1.
  • the outlet width b 2 of the centrifugal fan is in the example shown in Figure 2 embodiment of a two-sided suction or double-flow radial fan respectively on a half side of the radial impeller 2 related.
  • the exit width b 2 should relate to the blade outer diameter d 2 as 0.225 to 0.275: 1 and preferably as 0.25: 1.
  • the exit area F 2 of the radial fan can also be specified, ie the area dimension of the cylindrical rotating area enveloping the blade outer edges 20.
  • the exit surface F 2 is defined by the exit width b 2 and the blade outer diameter d 2 .
  • the entry surface F o of the radial impeller 2 ie the clear width of the inlet area of the cover plate 8 with the inlet diameter d o .
  • the entry area F o of the radial impeller 2 to its exit area F 2 should behave as 0.51 to 0.62: 1 and in particular as 0.56: 1.
  • An optimal dimensioning of the radial fan according to the invention must also take into account the proportions of the volute 1.
  • the entry surface F E of the inflow nozzle 5 and the cross section F A of the exit surface 16 of the volute casing 1 are of importance.
  • the size of the exit surface F A is ejected in FIG. 1 and the clear width F E of the inflow nozzle 5 in FIG. 2.
  • F E should behave like 0.67 to 0.71: 1 and especially 0.69: 1 to F A.
  • the number of blades 13 distributed over the circumference of the radial impeller 2 is important for the operating behavior of the radial fan according to the invention. This should be between ten and sixteen. In a preferred embodiment of the invention, twelve blades 13 are provided.
  • a radial fan according to the invention can be implemented equally in a one-sided as well as a two-sided suction arrangement, the latter being shown in FIG. 2. This design is preferred for air conditioners and air conditioners.
  • the invention provides a radial fan in which the degree of reaction as a quotient from static pressure to total pressure is very high. The proportion of kinetic energy that is initially unusable is therefore very small.
  • Fig. 8 shows the degree of reaction of the radial fan according to the invention in comparison to radial fans according to the prior art. The degree of reaction is plotted as a function of the number of volumes ⁇ at maximum efficiency ⁇ max ', ie at the optimum point ⁇ opt .
  • Fans according to the prior art are characterized by values 1 to 13 and the invention by the value 14. It can be seen that the value 14 according to the invention represents an optimal compromise between the demands for the largest possible number of volumes and a high degree of reaction.
  • the invention creates an arrangement in which the shaft power takes a maximum within the detected volume number range. It is therefore possible to design the drive motor of the radial fan for the maximum shaft power, so that an overload at operating points deviating from the design point is excluded. This advantageously distinguishes the radial fan according to the invention from a drum rotor fan with forwardly curved blades.
  • the shaft power increases with increasing volume flow, i.e. H. increasing volume ⁇ , progressively, and there is no maximum at all. With such a fan, there is always the risk of motor overload.
  • the maximum permissible peripheral speed of the radial fan according to the invention is approximately 85 m / sec. Such a high permissible peripheral speed enables the use of small fans for a given operating point, which is reflected in a reduction in investment costs. Because of the power density achieved, the radial fan according to the invention with a specific speed nq of approximately 80 is located in the area of the semi-axial fans.
  • a centrifugal fan with profiled blades (fan I) inclined outside the angular ranges according to the invention is compared with a centrifugal fan (fan II) according to the invention.
  • Constructive data such as dimensional relationships and number of blades are in the invention specified areas and correspond in each case, unless otherwise stated below.
  • the characteristic curve achieved according to the invention critically depends on the blade angles and the blade twist.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Jet Pumps And Other Pumps (AREA)

Claims (20)

1. Ventilateur radial formé d'un corps en spiral d'un rotor radial installé dans celui-ci, qui porte des aubes courbées en arrière à bords intérieurs du côté d'afflux dirigés obliquement par rapport à l'axe de rotation du rotor radial, disposées entre une plaque porteuse et une plaque de recouvrement s'appliquant avec un contour de déviation arrondi par dessus la buse d'afflux du ventilateur radial, le diamètre intérieur des aubes diminuant de la plaque de recouvrement vers la plaque porteuse et le diamètre intérieur moyen d1 des aubes étant dans un rapport d'environ 0,7: 1 avec le diamètre extérieur maximal d2 des aubes, caractérisé en ce que l'angle d'entrée (β1 D) des aubes, du côté de la plaque de recouvrement, est inférieur de 4° à 7° à l'angle d'entrée (ß1 T) des aubes du côté de la plaque porteuse, et l'angle de sortie (ß2 D) des aubes du côté de la plaque de recouvrement est inférieur de 3° à 6° à l'angle de sortie (g2 T) des aubes du côté de la plaque porteuse, et l'angle d'entrée (ß1 D) des aubes du côté de la plaque de recouvrement se situe entre 14° et 20° et l'angle de sortie (β2 D) des aubes du côté de la plaque de recouvrement, entre 39° et 45°.
2. Ventilateur radial selon la revendication 1, caractérisé en ce que l'angle d'entrée (ß1 D) des aubes du côté de la plaque de recouvrement est de 14,5° à 17,5° et l'angle d'entrée (ß1 T) des aubes du côté de la plaque porteuse, de 21,5°.
3. Ventilateur radial selon l'une des revendications 1 ou 2, caractérisé en ce que l'angle de sortie (ß2 D) des aubes du côté de la plaque de recouvrement est de 40° à 43° et que l'angle de sortie (ß2 T) des aubes du côté de la plaque porteuse est de 46°.
4. Ventilateur radial selon l'une des revendications. 1 à 3, caractérisé en ce que les aubes (13) sont tordues.
5. Ventilateur radial selon la revendication 4, caractérisé en ce que l'axe de torsion (22) des aubes (13) est situé dans leur région centrale.
6. Ventilateur radial selon la revendication 4, caractérisé en ce que l'axe de torsion (22) des aubes (13) est situé dans la région des bords extérieurs d'aubes (20).
7. Ventilateur radial selon l'une des revendications 4 à 6, caractérisé en ce que l'axe de torsion (22) est placé parallèlement à l'axe de rotation du rotor radial (2).
8. Ventilateur radial selon l'une des revendications 1 à 3, caractérisé en ce que les aubes (13) ne sont pas tordues et sont cisaillées transversalement à leur direction longitudinale.
9. Ventilateur radial selon l'une des revendications 1 à 8, caractérisé en ce que les aubes (13), vues de la plaque de recouvrement (8) vers la plaque porteuse (15), sont inclinées à l'envers du sens de rotation du rotor radial (2), de sorte que les bords intérieurs (19) des aubes font, en projection tangentielle et radiale, des angles aigus avec une normale à la plaque porteuse (15).
10. Ventilateur radial selon l'une des revendications 1 à 9, caractérisé en ce que les bords intérieurs (19) des aubes et/ou les bords extérieurs (20) des aubes ont une allure telle que leur projection dans un plan radial et dans le plan tangentiel correspondant sont dirigées obliquement par rapport à l'axe de rotation.
11. Ventilateur radial selon l'une des revendications 1 à 10, caractérisé en ce que le long de la largeur des aubes, les cordes de profil des coupes des aubes sont situées dans des plans différents.
12. Ventilateur radial selon l'une des revendications 1 à 11, caractérisé en ce que les aubes (13) sont formées par cintrage d'une pièce de tôle limitée par deux bords parallèles, les bords venant s'appliquer l'un contre l'autre à l'état monté avec formation d'un bord extérieur d'aube (20).
13. Ventilateur radial selon la revendication 1, caractérisé en ce que le diamètre d'entrée (do) de la plaque de recouvrement (8) est dans un rapport d'environ 0,75 : 1 avec le diamètre extérieur (dv des aubes.
14. Ventilateur radial selon la revendication 1, caractérisé en ce que le contour de déviation (11) de la plaque de recouvrement (8) a une courbure circulaire, parabolique ou hyperbolique, le ou les rayons de courbure (r) correspondants étant dans un rapport de (0,2 à 0,3) : 1 avec le diamètre d'entrée (d0).
15. Ventilateur radial selon la revendication 1, caractérisé en ce que la largeur de sortie (bV du rotor radial (2) est dans un rapport de (0,225 à 0,275) : 1 et, de préférence, de 0,25 :1 avec le diamètre extérieur (d2) des aubes.
16. Ventilateur radial selon la revendication 1. caractérisé en ce que la surface d'entrée (Fo) du rotor radial (2) est dans un rapport de (0,51 à 0,62) : 1 et, en particulier, de 0,56 : 1 avec sa surface de sortie (F2).
17. Ventilateur radial selon la revendication 1, caractérisé en ce que la largeur libre (FE) de la buse d'afflux est dans un rapport de (0,67 à 0,71) : 1 et, en particulier, de 0,69 : 1 avec la surface de sortie (FA) du corps en spirale (1).
18. Ventilateur radial selon la revendication 1, caractérisé en ce que le nombre des aubes (13) se situe entre dix et seize et qu'il est en particulier de douze.
19. Ventilateur radial selon l'une des revendications 1 à 18, caractérisé par une disposition aspirant des deux côtés, dans laquelle une plaque porteuse (15) disposée dans le plan médian du rotor radial (2) est garnie d'aubes (13) des deux côtés.
20. Utilisation d'un ventilateur radial selon l'une des revendications 1 à 19 pour des appareils de climatisation et des installations de climatisation.
EP82112081A 1982-12-29 1982-12-29 Ventilateur radial avec des aubes profilées courbées en arrière Expired EP0112932B1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
DE8282112081T DE3264089D1 (en) 1982-12-29 1982-12-29 Radial ventilator with backwards-curved profiled blades
EP82112081A EP0112932B1 (fr) 1982-12-29 1982-12-29 Ventilateur radial avec des aubes profilées courbées en arrière
AT82112081T ATE13711T1 (de) 1982-12-29 1982-12-29 Radialventilator mit rueckwaerts gekruemmten, profilierten schaufeln.
US06/565,656 US4526506A (en) 1982-12-29 1983-12-27 Radial fan with backwardly curving blades

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP82112081A EP0112932B1 (fr) 1982-12-29 1982-12-29 Ventilateur radial avec des aubes profilées courbées en arrière

Publications (2)

Publication Number Publication Date
EP0112932A1 EP0112932A1 (fr) 1984-07-11
EP0112932B1 true EP0112932B1 (fr) 1985-06-05

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP82112081A Expired EP0112932B1 (fr) 1982-12-29 1982-12-29 Ventilateur radial avec des aubes profilées courbées en arrière

Country Status (4)

Country Link
US (1) US4526506A (fr)
EP (1) EP0112932B1 (fr)
AT (1) ATE13711T1 (fr)
DE (1) DE3264089D1 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE9303711U1 (de) * 1993-03-13 1993-05-13 Babcock-BSH AG vormals Büttner-Schilde-Haas AG, 4150 Krefeld Radiallaufrad
WO2021089315A1 (fr) 2019-11-08 2021-05-14 Neuhäuser GmbH Dispositif de transport de pièces de préférence tabulaires, en particulier de manière horizontale
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DE9303711U1 (de) * 1993-03-13 1993-05-13 Babcock-BSH AG vormals Büttner-Schilde-Haas AG, 4150 Krefeld Radiallaufrad
WO2021089315A1 (fr) 2019-11-08 2021-05-14 Neuhäuser GmbH Dispositif de transport de pièces de préférence tabulaires, en particulier de manière horizontale
DE102019219914A1 (de) * 2019-12-17 2021-06-17 Ziehl-Abegg Se Strömungsmaschine und Verfahren zum Erfassen des Abströmwinkels bei Strömungsmaschinen
DE102021209605A1 (de) 2021-09-01 2023-03-02 Brose Fahrzeugteile SE & Co. Kommanditgesellschaft, Würzburg Lüfterrad für einen Radiallüfter

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EP0112932A1 (fr) 1984-07-11
DE3264089D1 (en) 1985-07-11
US4526506A (en) 1985-07-02
ATE13711T1 (de) 1985-06-15

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