EP2642130B1 - Roue pour transport axial des fluides, en particulier pour systèmes de réfrigération - Google Patents

Roue pour transport axial des fluides, en particulier pour systèmes de réfrigération Download PDF

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Publication number
EP2642130B1
EP2642130B1 EP13160281.5A EP13160281A EP2642130B1 EP 2642130 B1 EP2642130 B1 EP 2642130B1 EP 13160281 A EP13160281 A EP 13160281A EP 2642130 B1 EP2642130 B1 EP 2642130B1
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radius
impeller
edge
angle
blade
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German (de)
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EP2642130A1 (fr
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Leonardo Vitaletti
Roberto Lucchetti
Mariano Tartuferi
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Elica SpA
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Elica SpA
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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
    • F04D29/32—Rotors specially for elastic fluids for axial flow pumps
    • F04D29/38—Blades
    • F04D29/384—Blades characterised by form

Definitions

  • EP0259061A2 describes a prior art axial flow fan in accordance with the preamble of claim 1.
  • the impellers of the type indicated above have to meet needs of reduced bulk, reduced weights, manufacturing easiness, and cost effectiveness. From a performance point of view, higher and higher levels of fluido-dynamic efficiency and noiselessness are required.
  • the object of the present invention is to propose an axial impeller having such characteristics as to better meet the above-mentioned needs and to reconcile them to one another.
  • an axial impeller is generally indicated with the reference 1.
  • the impeller 1 has a plurality of, preferably five, blades 2 symmetrically connected to a hub 3 suitable for the connection of the impeller 1 to a shaft, the longitudinal axis of which forms the rotation axis R of the impeller 1.
  • the blades 2 of the impeller 1 are equal to one another, and it is therefore sufficient to determine the geometry of a single blade 2 and the hub 3 of the impeller 1, since the other blades 2 are obtained by rotation about the axis R of the reference blade by the angular pitch [360°/(number of blades)] of the blades.
  • the blade 2 of the impeller 1 is rigidly secured to the hub 3 that connects the blades 2 together and that can be, in turn, connected to a shaft suitable to rotate the impeller 1.
  • Each blade 2 forms a front surface 4 and an opposite back surface 5 connected together along a profile edge 6 made up of a radially outer apical edge 7, a side leading edge 8 that is the first to meet the flow F, a side trailing edge 9 opposite the leading edge 8, and joining edges 10 in the connection area of the blade 2 with the hub 3 (referred to as blade root).
  • the outer radius 13 of the impeller 1 is the radius of a circular circumference 14 circumscribing the impeller and tangent to the radially outermost points, referred to as shrouds 15, of the blades 2.
  • the inner radius 16 of the impeller 1 is the radius of an inner circular circumference 19 circumscribing the hub 3 and tangent to the connection points between the hub 3 and the blades 2 (referred to as blade roots 11). The difference between the outer radius 13 and the inner radius 16 defines the blade length.
  • a blade section is obtained for a given radius of the co-axial intersection cylinder.
  • the rectilinear segment joining the circumferentially extreme points of the blade section is referred to as the chord 29 of the section.
  • the length of the blade section, measured along the chord, is referred to as a length of chord at the radius at issue.
  • the angle of incidence 24 defines the angle formed by the chord of an impeller blade with the plane perpendicular to the rotation axis R.
  • the maximum axial dimension of the blade section denotes the maximum thickness of the section at the same radius.
  • the skew of the blade 2 indicates a displacement of each blade section along the helicoidal intersection line with the coaxial cylinder, measured by the generator at the section reference point.
  • a positive skew is oriented in a direction opposite the "forward" direction of rotation R of the impeller or, in other terms, going radially outwardly, the barycenter of the area of circumferential section of the blade moves to the direction opposite the "forward" direction of rotation R of the impeller 1.
  • the angle of inclination 27 denotes the angle between the direction of the flow (axial R) and the tangent to the blade surface in a point of a curve, defined by the intersection of a cylinder co-axial to the rotation axis R and the blade surface ( Figures 4 , 6 ).
  • the wrap angle 28 denotes, when seen in a projection axial on a plane normal to the rotation axis R, the angular width or the circumferential extension expressed in terms of the angle defined between two planes radial to the rotation axis R and tangent at the leading edge and at the trailing edge of the blade for the same radius.
  • the wrap angle 28 (Theta) defines the width of the blades in the circumferential direction, at a given radius R, particularly in the area comprised between the outer radius 13 and the intermediate radius 25 ( Fig. 1 ).
  • the leading edge 8 of the blade 2 when seen in a projection on a plane normal to the rotation axis R of the impeller 1 ( Fig. 1 ), is substantially rectilinear and extends in a direction radial to the rotation axis R, except for a rounded or beveled transition length between the leading edge 8 and the apical edge 7.
  • Such a beveled transition length has a very reduced extension of a few millimeters, both in the radial direction and in the circumferential direction relative to the rotation axis R.
  • the beveled length may have an extension from about 0.016*R1 to 0.063*R1, preferably from 0.031*R1 to 0.047*R1, even more preferably about 0.039*R1, both in the radial direction and in the direction circumferential relative to the rotation axis R, in which R1 is the outer radius of the impeller 1.
  • the apical edge 7 of the blade 2 is shaped like an arc of circle concentric to the rotation axis R, except for the above-mentioned rounded or beveled transition length between the leading edge 8 and the apical edge 7.
  • the trailing edge 9 of the blade 2 has a curved and concave shape, imparting to the blade 2 a positive skew and a continuous increase, approximately exponential, of the circumferential extension (axial projection of the length of chord) of the blade 2, as the radial distance relative to the rotation axis R increases.
  • a rounded or beveled transition length is formed, which may have a very reduced extension of a few millimeters both in the radial direction and in the circumferential direction relative to the rotation axis R.
  • the beveled length has an extension from about 0.016*R1 to 0.063*R1, preferably from 0.031*R1 to 0.047*R1, even more preferably about 0.039*R1, both in the radial direction and in the circumferential direction relative to the rotation axis R, in which R1 is the outer radius 13 of the impeller 1.
  • the joining edge 10 extends in the root area 11 of the blades 2 continuously and stepless from the trailing edge 9 of a blade 2 to the leading edge 8 of the adjacent blade 2.
  • a joining edge 10 preferably has an arc of circle shape, having a radius of between 0.12*R1 and 0.18*R1, preferably between 0.14*R1 and 0.16*R1, even more preferably about 0.15*R1, in which R1 is the outer radius 13 of the impeller 1, as well as an angular extension of between 160° and 180°, preferably between 170° and 175°.
  • the inner radius 16 of the impeller is within the range from 0.2*R1 to 0.3*R1, preferably from 0.25*R1 to 0.28*R1, even more preferably about 0.27*R1, in which R1 is the outer radius 13 of the impeller 1.
  • the blade 2 has a maximum circumferential extension (axial projection of the length of chord) at the apical edge 7 with an apical angle 17 (the angle defined between two planes radial to the rotation axis R that include together the total circumferential bulk of the apical edge 7 of the blade 2 on the leading side and on the trailing side) selected approximately within the range from 50° to 55°, preferably about 53°.
  • the total number of blades 2 is preferably 5, with a consequent angular pitch of 72°.
  • the blade 2 has a maximum axial bulk 18 ( Fig. 4 ) at the apical edge 7, or more precisely, at the transition lengths from the apical edge 7 to the leading 8 and trailing 9 edges.
  • a maximum axial bulk 18 can be selected within the range from 0.35*R1 to 0.40*R1, preferably from 0.37*R1 to 0.38*R1, even more preferably about 0.376*R1, in which R1 is the outer radius 13 of the impeller 1.
  • the maximum axial bulk 18 can be of about 47.8 mm.
  • the blade thickness is substantially constant over the entire extension of the blade 2.
  • the impeller 1 can be manufactured in metal sheet by cutting and cold deformation by a press or, alternatively, in synthetic material by injection molding with homogeneous thicknesses, promoting the control of the material shrinkage during the cooling thereof.
  • the hub 3 and the blades 2 are formed in a single piece and with a wall thickness that is substantially equal and uniform.
  • the hub 3 (or a hub 3 portion of the sheet or wall forming the impeller 1) may have the shape of a disc that is substantially planar and perpendicular to the rotation axis R.
  • the roots 11 of the blades 2 connect to the hub 2 along the inner circumference 19 in a single plane normal to the rotation axis R and, with further advantage, the hub 3 is substantially plane and lies in such a normal plane 20.
  • the blade 2 has a twisted portion 21 extending radially from the root 11 (inner circumference 19) up to a retroflection area or line 23 formed in the blade 2 at an intermediate circumference 22, and characterized by an extreme (maximum) angle of incidence 24 and an extreme local curvature (minimum radius of curvature) in the opposite direction to the torsion direction of the twisted portion 21, particularly at the leading 8 and trailing 9 edges.
  • a retroflection line 23 implements a reinforcement rib for the blade 2.
  • the twisted portion 21 has a twisted shape ("twisted" in the meaning of a twisting deformation) about an axis radial to the rotation axis R, obtaining a transition of the blade 2 shape and orientation from the root 11 (inner circumference 19) up to the retroflection area or line 23 (intermediate circumference 22).
  • the intermediate radius 25, i.e., the average radial distance between the rotation axis R and the retroflection line 23 of the blade 2 is preferably selected within the range from 0.42*R1 to 0.52*R1, preferably between 0.460*R1 and 0.480*R1, even more preferably about 0.472*R1, in which R1 is the outer radius 13 of the impeller 1.
  • R1 is the outer radius 13 of the impeller 1.
  • the intermediate radius 25 has preferably a length of 60mm.
  • the axial bulk 26 of the blade 2 at the retroflection line 23 is selected within the range from 0.6*Z1 to 0.65*Z1, preferably from 0.62*Z1 to 0.63*Z1, even more preferably about 0.628*Z1, wherein Z1 is the maximum axial bulk of the blade 2 at the apical edge 7.
  • Z1 is the maximum axial bulk of the blade 2 at the apical edge 7.
  • the axial bulk 26 at the retroflection line 23 may be of about 30 mm.
  • the axial bulk 26 at the retroflection line can be selected within the range from 0.21*R1 to 0.26*R1, preferably from 0.23*R1 to 0.24*R1, even more preferably about 0.236*R1, in which R1 is the outer radius 13 of the impeller 1.
  • R1 is the outer radius 13 of the impeller 1.
  • the axial bulk 26 at the retroflection line 23 can be of 30 mm.
  • the angle of inclination 27 at the leading edge 8 [Beta_LE] gradually increases starting from the retroflection line 23 and going radially outwardly up to the shroud 15 of the blade 2. Furthermore, starting from the retroflection line 23 and going radially outwardly up to the shroud 15 of the blade 2, the gradient of the angle of inclination 27 at the leading edge 8 [ ⁇ Beta_LE/ ⁇ R] decreases.
  • the trend of the angle of inclination 27 at the leading edge 8 follows a polynomial function starting from an initial value (at the intermediate radius 25) within the range between 55° and 58°, preferably about 56.4° and up to a final value (outer radius 13) within the range between 74° and 78°, preferably about 76.0°.
  • the angle of inclination 27 at the trailing edge 9 [Beta_TE] gradually increases starting from the retroflection line 23 and going radially outwardly up to close to the shroud 15 of the blade 2. Furthermore, starting from the retroflection line 23 and going radially outwardly up to the shroud 15 of the blade 2, also the gradient of the angle of inclination 27 at the trailing edge 9 [ ⁇ Beta_TE/ ⁇ R] decreases and, close to the shroud 15, such a gradient changes sign, since the angle of inclination 27 at the trailing edge 9 locally decreases close to the apical edge 7.
  • the trend 15 of the angle of inclination 27 at the leading edge 8 follows a polynomial function starting from an initial value (at the intermediate radius 25) within the range between 16.0° and 18.0°, preferably about 17.4°, and up to a final value (outer radius 13) within the range between 44° and 47°, preferably about 45.3°.
  • the difference between the angle of inclination 27 at the leading edge 8 and that at the trailing edge 9 for the same radius of the impeller [Beta_LE-Beta_TE] gradually decreases starting from the retroflection line 23 and going radially outwardly up to close to the shroud 15 of the blade 2. Furthermore, starting from the retroflection line 23 and going radially outwardly up to close to the shroud 15 of the blade 2, also the absolute value of the gradient of the difference in the angle of inclination 27 at the leading 8 and trailing 9 edges [ ⁇ (Beta_LE-Beta_TE)/ ⁇ R] decreases. Close to the shroud, such a gradient changes sign and becomes positive at the apical edge 7.
  • the trend of the difference in the angle of inclination 27 at the leading 8 and trailing 9 edges [Beta_LE-Beta_TE] follows a polynomial function starting from an initial value (at the intermediate radius 25) within the range between 38.0° and 40.0°, preferably about 39.0°, and up to a final value (outer radius 13) within the range between 29° and 32°, preferably about 30.7°.
  • the wrap angle 28 to the leading edge 8 [Theta_LE] is substantially zero from the retroflection line 23 up to the shroud 15 of the blade 2.
  • the wrap angle 28 at the trailing edge 9 [Theta_TE] gradually increases starting from the retroflection line 23 and going radially outwardly up to close to the shroud 15 of the blade 2.
  • the gradient of the wrap angle 28 at the trailing edge 9 [ ⁇ Theta_TE/ ⁇ R] increases continuously.
  • the trend of the wrap angle 28 at the trailing edge 9 follows a polynomial function starting from an initial value (at the intermediate radius 25) within the range between 29.0° and 32.0°, preferably about 30.6°, and up to a final value (outer radius 13) within the range between 55° and 57°, preferably about 56.1°.
  • the table 1 indicates the trend of the angles of inclination Beta_LE and Theta_LE at the leading and trailing edges and the relationships thereof.
  • a graphical representation of such values is provided in Fig. 5 .
  • the impeller 1 according to the invention has a number of advantages. It is particularly noiseless, it has a high degree of fluido-dynamic efficiency, can be easily manufactured, has a reduced overall weight and overall dimensions while keeping the energization of the processed flow constant.
  • the axial impeller 1 according to the invention is particularly suitable for conveying cooling flows in refrigeration systems.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Claims (14)

  1. Roue axiale (1) pour le transport de fluides, ladite roue (1) définissant un axe de rotation (R) et comprenant un moyeu (3) pour la connexion de la roue (1) à un arbre rotatif et une pluralité de pales de forme identique (2) connectées au moyeu (3) avec un pas angulaire constant,
    dans laquelle le rayon d'une circonférence extérieure (14) circonscrivant la roue (1) et tangent aux points radialement les plus extérieurs des pales (2) définit un rayon extérieur (13) de la roue (1),
    dans laquelle le rayon d'une circonférence intérieure (19) circonscrivant le moyeu (3) et tangent aux points de connexion entre le moyeu (3) et les pales (2) définit un rayon intérieur (16) de la roue (1),
    dans laquelle le rayon d'une circonférence intermédiaire (22) au niveau d'une section de pale avec angle d'incidence extrême (24) définit un rayon intermédiaire (25) de la roue (1), ledit rayon intermédiaire (25) étant supérieur au rayon intérieur (16) et inférieur au rayon extérieur (13),
    dans laquelle les pales (2) ont un bord de profil (6) formé par un bord apical radialement extérieur (7), un bord d'attaque (8) qui est le premier à rencontrer l'écoulement (F), un bord de fuite (9) opposé au bord d'attaque (8) et des bords de jonction (10) dans la zone de connexion de la lame (2) avec le moyeu (3),
    dans laquelle, lorsque vu dans une projection sur un plan normal à l'axe de rotation (R) :
    - le bord d'attaque (8) est sensiblement rectiligne et s'étend dans une direction radiale à l'axe de rotation (R),
    - le bord apical (7) a la forme d'un arc de cercle concentrique à l'axe de rotation (R),
    - le bord de fuite (9) a une forme incurvée et concave avec un angle d'enveloppement (28) qui augmente du rayon intermédiaire (25) jusqu'à proximité du rayon extérieur (13),
    - le bord de jonction (10) s'étend en continu et sans palier du bord de fuite (9) d'une pale (2) au bord d'attaque (8) de la pale adjacente (2),
    caractérisée en ce que le bord de jonction (10) a, lorsque vu dans une projection sur un plan normal à l'axe de rotation (R), une forme d'arc de cercle ayant une extension angulaire entre 160° et 180° et un rayon entre 0,12*R1 et 0,18*R1, dans lequel R1 est le rayon extérieur (13) de la roue (1).
  2. Roue axiale (1) selon la revendication 1, dans laquelle les pales (2) forment une portion torsadée (21) s'étendant radialement de la circonférence intérieure (19) jusqu'à une ligne de rétroflexion (23), ladite ligne de rétroflexion (23) étant formée au niveau de la circonférence intermédiaire (22) et ayant une courbure locale extrême dans la direction opposée à la direction de torsade de la portion torsadée (21), dans laquelle la ligne de rétroflexion (13) forme une nervure de renforcement pour la pale (2).
  3. Roue axiale (1) selon l'une des revendications précédentes, dans laquelle le bord de jonction (10) a, lorsque vu dans une projection sur un plan normal à l'axe de rotation (R), une forme d'arc de cercle concave ayant une extension angulaire entre 170° et 175° et un rayon entre 0,14*R1 et 0,16*R1, dans lequel R1 est le rayon extérieur (13) de la roue (1).
  4. Roue axiale (1) selon l'une des revendications précédentes, dans laquelle le rayon intérieur (16) est à l'intérieur de la plage de 0,2*R1 à 0,3*R1, dans lequel R1 est le rayon extérieur (13) de la roue (1).
  5. Roue axiale (1) selon l'une des revendications précédentes, dans laquelle le nombre total de pales (2) est de cinq et, lorsque vu dans une projection sur un plan normal à l'axe de rotation (R), la pale (2) a une extension circonférentielle maximum au niveau du bord apical (7) avec un angle apical (17) de 50° à 55°.
  6. Roue axiale (1) selon l'une des revendications précédentes, dans laquelle la pale (2) a un volume axial maximum (18) au niveau du bord apical (7), ledit volume axial maximum (18) étant sélectionné à l'intérieur de la plage de 0,35*R1 à 0,40*R1, dans lequel R1 est le rayon extérieur (13) de la roue (1).
  7. Roue axiale (1) selon l'une des revendications précédentes, dans laquelle l'épaisseur de la pale est sensiblement uniforme sur toute l'extension de la pale (2).
  8. Roue axiale (1) selon l'une des revendications précédentes, dans laquelle le rayon intermédiaire (25) est sélectionné à l'intérieur de la plage de 0,42*R1 à 0,52*R1, dans lequel R1 est le rayon extérieur (13) de la roue (1).
  9. Roue axiale (1) selon l'une des revendications précédentes, dans laquelle le volume axial (26) de la pale (2) au niveau du rayon intermédiaire est sélectionné à l'intérieur de la plage de 0,6*Z1 à 0,65*Z1, dans lequel Z1 est le volume axial maximum de la pale (2) au niveau du bord apical (7).
  10. Roue axiale (1) selon l'une des revendications précédentes, dans laquelle le volume axial (26) au niveau du rayon intermédiaire est sélectionné à l'intérieur de la plage de 0,21*R1 à 0,26*R1, dans lequel R1 est le rayon extérieur (13).
  11. Roue axiale (1) selon l'une des revendications précédentes, dans laquelle, du rayon intermédiaire (25) jusqu'au rayon extérieur (13), l'angle d'inclinaison (27) au niveau du bord d'attaque (8) augmente progressivement et le gradient de l'angle d'inclinaison (27) au niveau du bord d'attaque (8) diminue, dans laquelle au niveau du rayon intermédiaire (25), l'angle d'inclinaison (27) au niveau du bord d'attaque (8) est à l'intérieur de la plage entre 55° et 58°,
    dans laquelle au niveau du rayon extérieur (13), l'angle d'inclinaison (27) au niveau du bord d'attaque (8) est à l'intérieur de la plage entre 74° et 78°.
  12. Roue axiale (1) selon l'une des revendications précédentes, dans laquelle l'angle d'inclinaison (27) au niveau du bord de fuite (9) augmente progressivement du rayon intermédiaire (25) jusqu'à proximité du rayon extérieur (13) et diminue localement au niveau du bord apical (7),
    dans laquelle le gradient de l'angle d'inclinaison (27) au niveau du bord de fuite (9) diminue du rayon intermédiaire (25) jusqu'au rayon extérieur (13) et change de signe au niveau du bord apical (7),
    dans laquelle au niveau du rayon intermédiaire (25), l'angle d'inclinaison (27) au niveau du bord d'attaque (8) est à l'intérieur de la plage entre 16,0° et 18,0°,
    dans laquelle au niveau du rayon extérieur (13), l'angle d'inclinaison (27) au niveau du bord d'attaque (8) est à l'intérieur de la plage entre 44° et 47°.
  13. Roue axiale (1) selon l'une des revendications précédentes, dans laquelle la différence entre l'angle d'inclinaison (27) au niveau du bord d'attaque (8) et au niveau du bord de fuite (9) pour le même rayon de la roue diminue du rayon intermédiaire (25) jusqu'à proximité du rayon extérieur (13),
    dans laquelle, au niveau du rayon intermédiaire (25), la différence d'angle d'inclinaison (27) au niveau du bord d'attaque (8) et du bord de fuite (9) est à l'intérieur de la plage entre 38,0° et 40,0°,
    dans laquelle, au niveau du rayon extérieur (13), la différence d'angle d'inclinaison (27) au niveau du bord d'attaque (8) et du bord de fuite (9) est à l'intérieur de la plage entre 29° et 32°.
  14. Roue axiale (1) selon l'une des revendications précédentes, dans laquelle, du rayon intermédiaire (25) jusqu'à proximité du rayon extérieur (13), le gradient de l'angle d'enveloppement (28) au niveau du bord de fuite (9) augmente,
    dans laquelle, au niveau du rayon intermédiaire (25), l'angle d'enveloppement (28) au niveau du bord de fuite (9) est à l'intérieur de la plage entre 29,0° et 32,0°,
    dans laquelle, au niveau du rayon extérieur (13), l'angle d'enveloppement (28) au niveau du bord de fuite (9) est à l'intérieur de la plage entre 55° et 57°.
EP13160281.5A 2012-03-22 2013-03-21 Roue pour transport axial des fluides, en particulier pour systèmes de réfrigération Active EP2642130B1 (fr)

Applications Claiming Priority (1)

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IT000451A ITMI20120451A1 (it) 2012-03-22 2012-03-22 Girante per il convogliamento assiale di fluidi, in particolare per sistemi di refrigerazione

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EP2642130B1 true EP2642130B1 (fr) 2019-04-17

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MY182874A (en) * 2013-10-01 2021-02-05 Sharp Kk Propeller fan and blower
CN106903875A (zh) * 2017-03-16 2017-06-30 青岛科技大学 一种3d打印用小型螺杆塑化装置
CN113847275B (zh) * 2021-08-30 2023-06-16 珠海格力电器股份有限公司 翼型轴流风叶及空调外机
CN113898607B (zh) * 2021-09-30 2023-07-28 江苏徐工工程机械研究院有限公司 叶轮机械的叶片相贯线、叶片的设计方法及叶轮机械的叶片
CN115111194B (zh) * 2022-06-27 2024-05-10 约克广州空调冷冻设备有限公司 叶片及使用其的轴流叶轮

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ITMI20120451A1 (it) 2013-09-23
EP2642130A1 (fr) 2013-09-25

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