EP0303543B1 - Cross-flow fan - Google Patents

Cross-flow fan Download PDF

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Publication number
EP0303543B1
EP0303543B1 EP88402086A EP88402086A EP0303543B1 EP 0303543 B1 EP0303543 B1 EP 0303543B1 EP 88402086 A EP88402086 A EP 88402086A EP 88402086 A EP88402086 A EP 88402086A EP 0303543 B1 EP0303543 B1 EP 0303543B1
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EP
European Patent Office
Prior art keywords
impeller
cross
axis
upstream
leading edge
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EP88402086A
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German (de)
French (fr)
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EP0303543A1 (en
Inventor
Jean-Pierre Guezou
Gilles Heid
Pierre Bailleux
Marc Pruvost
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Direction General pour lArmement DGA
Office National dEtudes et de Recherches Aerospatiales ONERA
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Direction General pour lArmement DGA
Office National dEtudes et de Recherches Aerospatiales ONERA
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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
    • F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D17/02—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps having non-centrifugal stages, e.g. centripetal
    • F04D17/04—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps having non-centrifugal stages, e.g. centripetal of transverse-flow type

Definitions

  • the technical sector of the present invention is that of transverse current fans applied to the ventilation of a room or a machine or else to the support of an air cushion vehicle, for example a surface effect vessel. .
  • This type of ventilator is well known and was first proposed in 1892 by MORTIER for the ventilation of coal mines.
  • the main feature of this fan is that it has a hunchback type pressure-flow characteristic, the increasing part of which represents between 50 and 75% of the maximum range (or excursion) accessible in flow.
  • the second feature is to present a pressure at zero flow other than zero.
  • Another characteristic of this fan lies in the simultaneous supply of high flow and pressure coefficients, compared to the centrifugal fan which provides, at equal size, only a high pressure coefficient with low flow coefficient and to the axial fan which does not provides on the other hand, at equal size, that a high flow coefficient with a low pressure coefficient.
  • the weak point of this fan traditionally resides in the efficiency obtained which can be improved by playing on the stator shapes.
  • patent DE-A-1 428 071 is known relating to a transverse fan having a characteristic characteristic of stable air flow and being very noisy.
  • Patent DE-A-2 545 036 is also known, improving the fan of the previous patent by a complex system of guide walls and porous walls placed on the path of the fluid to reduce noise.
  • this advantage can be compromised by the fouling of the porous walls after a certain period of use.
  • Patent FR-A-2 481 378 is also known, which aims to reduce the noise level and to provide an increased air flow for the same rotor speed by a particular rounded shape of the downstream volute and volute nozzles and lacrosse.
  • the flow properties of the transverse fan are mainly used and no attempt has ever been made to improve the shapes of the upstream collector and the downstream diffuser to simultaneously obtain a high flow and pressure, while aiming for high efficiency.
  • the aim of the present invention is therefore to define, for the first time, a transverse fan whose characteristics are provided in advance, in order to simultaneously obtain in a technical installation coefficients of flow and pressure which can reach respectively 2.5 to 3 approximately, while controlling the stability of the operating point over the entire flow range and in particular over the increasing part of the pressure-flow characteristic on which it is known that a pumping phenomenon can arise. It is known that such a pumping phenomenon results in periodic pulses in flow and pressure in the downstream circuit, characterized by a pumping frequency and amplitude, which makes the machine unusable in an industrial application.
  • the stock element has between its upstream and downstream nozzles a thickness of between 1 and 40% of the outside diameter De of the wheel.
  • the thickness of the stock element is 16% of the outside diameter De of the wheel.
  • the stock-wheel face is flat and inclined with respect to the ordinate axis at an angle between _20 and 60 °.
  • the stock / wheel face is hollow and produced in the form of an arc of a circle passing through the upstream and downstream beaks of stock element, both placed on a parallel to the Y axis, such that the tangent to the upstream beak delimits an angle with said parallel to the ordinate axis varying between 0 to 60 °.
  • the length (1) of the upstream face of the butt projected onto the abscissa axis is between 90 and 100% of the outside diameter De of the wheel.
  • the upstream face of the butt consists of a flat surface inclined at an angle between 25 and 80 ° relative to the axis of the abscissa.
  • the angle of inclination is equal to 26 ° and the length (1) to 95% of the outside diameter De of the wheel.
  • the upstream stock face consists of an arc of a circle open towards the wheel whose tangent to the upstream stock spout defines with respect to the radius passing through the upstream spout an angle of between 25 and 80 °.
  • the downstream volute is extended by a divergent delimiting an angle of 7 ° relative to the abscissa axis from a point located on a parallel to the ordinate axis passing through the downstream butt stock at a distance from that -this between 60 and 90% of the outside diameter De of the wheel.
  • the downstream volute is delimited in section by a first arc of a circle concentric with the wheel and a second arc of circle connecting the first arc of circle to the divergent.
  • the downstream volute passes through an axis situated on a parallel to the X axis passing through the downstream butt of the butt, at a distance from the latter between 60 and 120% of the external diameter De of the wheel.
  • This distance is equal to 59% of the outside diameter De of the wheel.
  • the wheel is of the type with sharp blades, the internal diameter of which is between 70 and 80% of its external diameter, and each blade has, depending on the external diameter De of the wheel, a radius of curvature of between 10 and 15% , a rope between 10 and 15% and an elongation between 1 and 5.
  • the blades are twisted longitudinally with a helix angle of less than 10 °.
  • the wheel is twisted by rotation of the end plates relative to one another.
  • the butt end element is twisted with a helix angle of less than 10 °.
  • a result of the present invention lies in obtaining a high yield which reaches 70 to 80%.
  • Another result lies in taking advantage of the intrinsic characteristics of the transverse fan to obtain a sheet flow or an air curtain; the flow rate being therefore proportional to the length of the wheel, at constant speed, the value of the reduced aeraulic coefficients is kept.
  • Another result is the increase in the pumping margin.
  • Another result lies in the accessibility to powers of the order of megawatts, while retaining a minimum size compared to that of conventional machines of the same power.
  • the characteristics of a fan are usually defined by the dimensionless coefficients of flow Cd, pressure Cp and efficiency ⁇ according to the relationships: where L is the length of the wheel (m), ⁇ the speed of rotation of the wheel (rd / s), R the radius of the wheel, ⁇ the density of the air (Kg / m3), Qv the flow of the fan (m3 / s) and ⁇ P the pressure variation (Pa).
  • FIG 1 there is shown an embodiment of a transverse fan comprising a wheel 1, rotating in the direction of the arrow F, a stock member 2 and a scroll element 3.
  • the scroll and butt elements constitute the stator of the rotary machine and delimit an upstream part of converging section and a downstream part 4a of diverging section, the latter being followed by a use circuit 4b partially shown.
  • the stock element 2 comprises an upstream face 5 or upstream volute, an upstream spout 6, a wheel-stock face 7, a spout downstream 8 and a downstream face 9.
  • the scroll element 3 comprises an upstream face 10, a scroll beak 11 and a downstream scroll 12.
  • the upstream butt 6 of the butt is placed at a distance from the wheel 1 called the butt 13 of the butt (ECR).
  • the volute nozzle 11 is also placed at a distance from the wheel 1 called volute nozzle air gap 14 (EVR).
  • the position of the upstream spout 6 of the butt is defined, in accordance with FIG. 2, by the angle A BCAM between the axis X and the radius D of the wheel 1 passing through this spout.
  • This angle can be between 290 and 330 °.
  • this angle is 309 ° with zero air gap.
  • the dimension of the air gap 13 is between 2 and 8% of the outside diameter De of the wheel and more particularly between 2 and 3%.
  • the thickness Ec of the stock and its inclination A FRC with respect to the parallel 15 to the axis Y passing through the upstream nozzle 6 of the stock has been shown diagrammatically as the gap ECR zero.
  • the thickness Ec is counted between the planar downstream face 9 and the plane 16 parallel to this face passing through the spout 6.
  • the thickness Ec is between 0.1 and 40% of the external diameter De of the wheel 1 and advantageously between 14 and 18%.
  • the face 7 of the wheel-stock can be either flat or hollow, in order to organize the internal flow of air as a function of the envisaged application.
  • the butt-wheel face 7a shown in FIG. 3, is flat and wedged at an angle A FRC , with respect to the parallel 15, between _30 and + 60 ° and more particularly between _10 and + 10 °.
  • the butt-wheel face 7b represented in FIG. 4, is hollow, in an arc of a circle, the upstream spout 6 and the downstream spout 8 of the butt being in this configuration aligned on the parallel 17 to the axis Y.
  • the center B of curvature of this arc of circle is located on the perpendicular bisector of the cord 18 joining the beaks 6 and 8 and the angle A FRC is determined by the tangent 19 passing through the beak 6 and the cord 18. This angle is between 0 and 60 ° and advantageously between 10 and 25 °. Note that when the angle A FRC is zero, the face 7b is plane.
  • the upstream face 5 of the stock can be either flat 5a (FIG. 5) or hollow 5b (FIG. 6). It extends between the upstream nozzle 6 of the butt and a point M FAC .
  • the face 5a is defined by its angular position relative to the axis X and by its length projected on this same axis.
  • the angle A FAC is between 25 and 80 ° and its projected length (1) is between 90 and 100% of the outside diameter De of the wheel 1.
  • the hollow face 5b is defined by the angle A ′ FAC between the radius of the wheel passing through the upstream nozzle 6 of the stock and the tangent at this point to the shape studied.
  • the angle A ′ FAC is between 25 and 80 ° as above and more particularly between 60 and 78 °.
  • the center C of curvature is located on the perpendicular bisector of the cord 20 passing the beak 6 and the point M FAC .
  • the length (1) of the hollow face projected on an axis parallel to the axis X is between 90 and 100% of the external diameter De of the wheel 1.
  • the volute beak 11 the position of which is shown diagrammatically in FIG. 7, is located on a circular arc 21, at a distance or air gap 14 (EVR) of between 2 and 8% of the external diameter De of the wheel 1.
  • EMR air gap 14
  • L 'arc of a circle 21 is delimited by the angle A BC between 76 and 112 °.
  • This figure also shows the upstream face 10 of the volute beak inclined by the angle A FABV relative to the radius passing through the volute beak 11.
  • the angle A FABV is between 0 and 70 °. These two angles are chosen so as to ensure an optimal supply compatible with the nominal point sought.
  • FIG. 8 represents the downstream volute 12 which is consisting of three parts 21, 22 and 23.
  • Part 21 is an arc always concentric with the wheel 1 and exists when the angle A BC is less than 112 °.
  • the two parts 22 and 23 are defined from the stock element 2 by delimiting a first section denoted SHBCAV (horizontal section of downstream stock tip) parallel to the axis X, such that its length is between 80 and 100 % of the outside diameter De of the wheel 1, and a second section denoted SBCAV (vertical section of downstream butt stock), such that its length is between 60 and 90% of the outside diameter Of the wheel 1.
  • SHBCAV horizontal section of downstream stock tip
  • SBCAV vertical section of downstream butt stock
  • the volute is finally connected to the divergent plane 24 by the planar part 23 extending the latter.
  • the divergent 4b is delimited by a flat surface extending the downstream face 9 of the butt and the flat part 24 making an angle of 7 ° with the axis X. This leads to a fan divergent at 7 °, a value commonly accepted in mechanical mechanics. fluids with regard to obtaining a minimum pressure drop.
  • the wheel of a transverse fan is defined in a known manner by the following parameters: outside and inside diameters, length, number of blades, radius of curvature of the blade, chord of the blade, angles of entry and exit of the blade , flange diameter.
  • outside and inside diameters outside and inside diameters
  • length length
  • number of blades radius of curvature of the blade
  • chord of the blade chord of the blade
  • angles of entry and exit of the blade flange diameter
  • the wheel 1 can be twisted as shown in FIG. 10 by rotation of the flanges 26 and 27 relative to each other by a helix angle A H.
  • the leading edge 28 of each blade 25 then defines a curve having a helix angle A H less than 10 °. This achievement makes it possible, among other things, to reduce the noise and the amplitude of the vibrations.
  • the line described by the volute beak 11 and / or the upstream beak 6 of the butt can be twisted according to the same law.
  • E C / De 16.25%
  • a FRC 0 °
  • a FAC with minimum air gap 40 °
  • Radius of curvature of the upstream stock volute 251 mm
  • a FABV with minimum air gap 40 °
  • S HBCAV with minimum air gap 166 mm or 58.64% of De
  • S VBCAV with minimum air gap 220 mm or 77.73% of De
  • the power obtained is approximately 2 KWatt for a fan 420 mm long, while obtaining a power equivalent using an axial or centrifugal fan would require a diameter and a length of at least 2 to 3 times larger.
  • the ⁇ P and Qv values are measured at the fan outlet.
  • Curve P represents the pressure variation and curve R the efficiency.
  • this fan has an increased pumping margin ⁇ Q compared to conventional machines with a hunchback curve and can be used in a range of flow excursion free of pumping risks.
  • this margin ⁇ Q is of the order of 1 m3 / s. This type of ventilator can therefore be used in particular in the lifting of surface effect vessels.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Control Of Motors That Do Not Use Commutators (AREA)

Description

Le secteur technique de la présente invention est celui des ventilateurs à courant transversal appliqués à la ventilation d'un local ou d'une machine ou bien à la sustentation d'un véhicule à coussin d'air, par exemple un navire à effet de surface.The technical sector of the present invention is that of transverse current fans applied to the ventilation of a room or a machine or else to the support of an air cushion vehicle, for example a surface effect vessel. .

Ce type de ventilateur est bien connu et a été proposé pour la première fois en 1892 par MORTIER pour la ventilation des mines de charbon. La particularité principale de ce ventilateur est de présenter une caractéristique pression-débit de type bossu, dont la partie croissante représente entre 50 et 75% de la plage maximale (ou excursion) accessible en débit. La seconde particularité est de présenter une pression à débit nul différente de zéro. Une autre caractéristique de ce ventilateur réside dans la fourniture simultanée de coefficients de débit et de pression élevés, comparativement au ventilateur centrifuge qui ne fournit, à taille égale, qu'un coefficient de pression élevé à coefficient de débit faible et au ventilateur axial qui ne fournit par contre, à taille égale, qu'un coefficent de débit élevé à coefficient de pression faible. En conséquence, la puissance aéraulique fournie par le ventilateur transverse est alors nettement supérieure. Le point faible de ce ventilateur réside traditionnellement dans le rendement obtenu qui peut être amélioré en jouant sur les formes statoriques.This type of ventilator is well known and was first proposed in 1892 by MORTIER for the ventilation of coal mines. The main feature of this fan is that it has a hunchback type pressure-flow characteristic, the increasing part of which represents between 50 and 75% of the maximum range (or excursion) accessible in flow. The second feature is to present a pressure at zero flow other than zero. Another characteristic of this fan lies in the simultaneous supply of high flow and pressure coefficients, compared to the centrifugal fan which provides, at equal size, only a high pressure coefficient with low flow coefficient and to the axial fan which does not provides on the other hand, at equal size, that a high flow coefficient with a low pressure coefficient. As a result, the air power supplied by the transverse fan is then significantly higher. The weak point of this fan traditionally resides in the efficiency obtained which can be improved by playing on the stator shapes.

A titre indicatif, on connaît le brevet DE-A-1 428 071 relatif à un ventilateur transverse ayant une caractéristique de débit d'air stable et étant peu bruyant.By way of indication, patent DE-A-1 428 071 is known relating to a transverse fan having a characteristic characteristic of stable air flow and being very noisy.

On connaît également le brevet DE-A-2 545 036 perfectionnant le ventilateur du brevet précédent par un système complexe de parois-guides et de parois poreuses placées sur le trajet du fluide pour réduire le bruit. Cependant, cet avantage peut être compromis par l'encrassement des parois poreuses après un certain temps d'utilisation.Patent DE-A-2 545 036 is also known, improving the fan of the previous patent by a complex system of guide walls and porous walls placed on the path of the fluid to reduce noise. However, this advantage can be compromised by the fouling of the porous walls after a certain period of use.

On connaît encore le brevet FR-A-2 481 378 qui vise à réduire le niveau de bruit et à fournir un débit d'air accru pour une même vitesse du rotor par une forme particulière en arrondi de la volute aval et des becs de volute et de crosse.Patent FR-A-2 481 378 is also known, which aims to reduce the noise level and to provide an increased air flow for the same rotor speed by a particular rounded shape of the downstream volute and volute nozzles and lacrosse.

On notera toutefois que ces trois documents concernent des appareils domestiques, où le débit d'air est inférieur à 0,05 m³/s avec une pression inférieure à 50 Pa.However, it should be noted that these three documents relate to household appliances, where the air flow rate is less than 0.05 m³ / s with a pressure less than 50 Pa.

On connaît encore un dispositif de ventilation des radiateurs de fluide et des rhéostats d'une motrice à l'aide d'un ventilateur transverse. Cependant, il s'agit surtout de l'incorporation de ce ventilateur dans une structure où l'espace est réduit.There is also known a device for ventilating fluid radiators and rheostats of an engine using a transverse fan. However, it is above all the incorporation of this fan in a structure where space is reduced.

Dans ces réalisations antérieures, on utilise surtout les propriétés de débit du ventilateur transverse et on n'a jamais cherché à améliorer les formes du collecteur amont et du diffuseur aval pour obtenir simultanément un débit et une pression élevés, tout en visant un rendement élevé.In these previous embodiments, the flow properties of the transverse fan are mainly used and no attempt has ever been made to improve the shapes of the upstream collector and the downstream diffuser to simultaneously obtain a high flow and pressure, while aiming for high efficiency.

Une première tentative a été faite dans une étude théorique publiée par G. HEID, Revue française de mécanique 1986-2, sur l'application de la théorie de BIDARD relative au pompage des compresseurs, à l'étude du phénomène de pompage dans les ventilateurs transverses. En effet, toutes les réalisations connues des ventilateurs transverses sont des configurations figées répondant à un problème spécifique de débit; l'homme de l'art ne peut donc pas à partir de ces réalisations extrapoler les résultats obtenus. Cette étude a donc permis de formuler les conclusions suivantes:

  • du point de vue pression, le rotor se comporte comme un seul étage, ce qui a pour avantage de donner la possibilité d'augmenter le débit en augmentant sa longueur,
  • seule la dissymétrie amont/aval des formes statoriques détermine le sens d'écoulement,
  • pour un même couple pression/débit, on peut choisir plusieurs combinaisons diamètre/longueur/vitesse de rotation du rotor.
A first attempt was made in a theoretical study published by G. HEID, Revue française de Mécanique 1986-2, on the application of BIDARD theory relating to pumping of compressors, to the study of the phenomenon of pumping in fans. transverse. Indeed, all the known embodiments of transverse fans are fixed configurations responding to a specific problem of flow; those skilled in the art cannot therefore extrapolate the results obtained from these achievements. This study therefore made it possible to draw the following conclusions:
  • from the pressure point of view, the rotor behaves as a single stage, which has the advantage of giving the possibility of increasing the flow rate by increasing its length,
  • only the upstream / downstream asymmetry of the stator shapes determines the direction of flow,
  • for the same pressure / flow couple, it is possible to choose several combinations of diameter / length / speed of rotation of the rotor.

Le but de la présente invention est donc de définir, pour la première fois, un ventilateur transverse dont les caractéristiques sont prévues à l'avance, pour obtenir simultanément dans une installation technique des coefficients de débit et de pression pouvant atteindre respectivement 2,5 à 3 environ, tout en maftrisant la stabilité du point de fonctionnement sur l'ensemble de la plage de débit et en particulier sur la partie croissante de la caractéristique pression-débit sur laquelle on sait qu'un phénomène de pompage peut prendre naissance. Il est connu qu'un tel phénomène de pompage se traduit par des pulsations périodiques en débit et en pression dans le circuit aval, caractérisées par une fréquence et une amplitude de pompage, ce qui rend la machine inutilisable dans une application industrielle.The aim of the present invention is therefore to define, for the first time, a transverse fan whose characteristics are provided in advance, in order to simultaneously obtain in a technical installation coefficients of flow and pressure which can reach respectively 2.5 to 3 approximately, while controlling the stability of the operating point over the entire flow range and in particular over the increasing part of the pressure-flow characteristic on which it is known that a pumping phenomenon can arise. It is known that such a pumping phenomenon results in periodic pulses in flow and pressure in the downstream circuit, characterized by a pumping frequency and amplitude, which makes the machine unusable in an industrial application.

L'invention a donc pour objet un ventilateur à courant transversal comportant un collecteur amont délimité par une face amont d'élément de volute et une face amont d'élément de crosse, une roue ou rotor munie de pales et un divergent délimité par une face aval de l'élément de volute et une face aval de l'élement de crosse, le collecteur et le divergent délimitant en regard de la roue dans un plan perpendiculaire à son axe de rotation deux passages longitudinaux rétrécis définis d'une part, par un bec de l'élément de volute et d'autre part, par un bec amont de l'élément de crosse, caractérisé en ce que dans un référentiel d'axes perpendiculaires dont l'origine est située sur l'axe de rotation de la roue et dont l'axe des abscisses est parallèle à la face aval de l'élément de crosse, il présente:

  • un bec amont de l'élément de crosse décrivant un angle compris entre 290 et 330° à une distance de la roue ou entrefer comprise entre 2 et 8% du diamètre extérieur De de la roue,
  • une face de l'élément de crosse décrivant un angle dont le sommet est confondu avec le bec amont de crosse compris entre _20° et 60° par rapport à un axe parallèle à l'axe des ordonnées concourant avec le bec amont,
  • un bec de volute décrivant un angle compris entre 76 et 112° à une distance de la roue ou entrefer comprise entre 2 et 8% du diamètre extérieur De de la roue,
  • une face amont plane, concourante au bec de volute, et inclinée par rapport au plan joignant l'axe de rotation de la roue et le bec de volute d'un angle d'une valeur comprise entre 0 et 70°.
The subject of the invention is therefore a transverse current fan comprising an upstream collector delimited by an upstream face of a volute element and an upstream face of a stock element, a wheel or rotor provided with blades and a divergent delimited by a face. downstream of the volute element and a downstream face of the stock element, the manifold and the divergent delimiting opposite the wheel in a plane perpendicular to its axis of rotation two narrowed longitudinal passages defined on the one hand by a beak of the volute element and on the other hand, by a beak upstream of the stock element, characterized in that in a reference frame of perpendicular axes whose origin is located on the axis of rotation of the wheel and whose abscissa axis is parallel to the downstream face of the stock element, it has:
  • an upstream nozzle of the stock element describing an angle between 290 and 330 ° at a distance from the wheel or air gap between 2 and 8% of the outside diameter De of the wheel,
  • a face of the stock element describing an angle whose apex coincides with the upstream stock spout between _20 ° and 60 ° relative to an axis parallel to the ordinate axis competing with the upstream stock,
  • a volute beak describing an angle between 76 and 112 ° at a distance from the wheel or air gap between 2 and 8% of the outside diameter De of the wheel,
  • a flat upstream face, concurrent with the volute beak, and inclined relative to the plane joining the axis of rotation of the wheel and the volute beak by an angle of a value included between 0 and 70 °.

L'élément de crosse présente entre ses becs amont et aval une épaisseur comprise entre 1 et 40% du diamètre extérieur De de la roue.The stock element has between its upstream and downstream nozzles a thickness of between 1 and 40% of the outside diameter De of the wheel.

L'épaisseur de l'élément de crosse est égale à 16% du diamètre extérieur De de la roue.The thickness of the stock element is 16% of the outside diameter De of the wheel.

La face crosse-roue est plane et inclinée par rapport à l'axe des ordonnées d'un angle compris entre _20 et 60°.The stock-wheel face is flat and inclined with respect to the ordinate axis at an angle between _20 and 60 °.

La face crosse/roue est creuse et réalisée sous la forme d'un arc de cercle passant par les becs amont et aval d'élément de crosse placés tous deux sur une parallèle à l'axe Y, tel que la tangente au bec amont délimite un angle avec ladite parallèle à l'axe des ordonnées variant entre 0 à 60°.The stock / wheel face is hollow and produced in the form of an arc of a circle passing through the upstream and downstream beaks of stock element, both placed on a parallel to the Y axis, such that the tangent to the upstream beak delimits an angle with said parallel to the ordinate axis varying between 0 to 60 °.

La longueur (1) de la face amont de crosse projetée sur l'axe des abscisses est comprise entre 90 et 100% du diamètre extérieur De de la roue.The length (1) of the upstream face of the butt projected onto the abscissa axis is between 90 and 100% of the outside diameter De of the wheel.

La face amont de crosse est constituée par une surface plane inclinée d'un angle compris entre 25 et 80° par rapport à l'axe des abscisses.The upstream face of the butt consists of a flat surface inclined at an angle between 25 and 80 ° relative to the axis of the abscissa.

L'angle d'inclinaison est égal à 26° et la longueur (1) à 95% du diamètre extérieur De de la roue.The angle of inclination is equal to 26 ° and the length (1) to 95% of the outside diameter De of the wheel.

La face amont de crosse est constituée d'un arc de cercle ouvert vers la roue dont la tangente au bec amont de crosse délimite par rapport au rayon passant par le bec amont un angle compris entre 25 et 80°.The upstream stock face consists of an arc of a circle open towards the wheel whose tangent to the upstream stock spout defines with respect to the radius passing through the upstream spout an angle of between 25 and 80 °.

La volute aval est prolongée par un divergent délimitant un angle de 7° par rapport à l'axe des abscisses à partir d'un point situé sur une parallèle à l'axe des ordonnées passant par le bec de crosse aval à une distance de celui-ci comprise entre 60 et 90% du diamètre extérieur De de la roue.The downstream volute is extended by a divergent delimiting an angle of 7 ° relative to the abscissa axis from a point located on a parallel to the ordinate axis passing through the downstream butt stock at a distance from that -this between 60 and 90% of the outside diameter De of the wheel.

La volute aval est délimitée en section par un premier arc de cercle concentrique à la roue et un second arc de cercle reliant le premier arc de cercle au divergent.The downstream volute is delimited in section by a first arc of a circle concentric with the wheel and a second arc of circle connecting the first arc of circle to the divergent.

La volute aval passe par un axe situé sur une parallèle à l'axe des X passant par le bec aval de crosse, à une distance de ce dernier comprise entre 60 et 120% du diamètre extérieur De de la roue.The downstream volute passes through an axis situated on a parallel to the X axis passing through the downstream butt of the butt, at a distance from the latter between 60 and 120% of the external diameter De of the wheel.

Cette distance est égale à 59% du diamètre extérieur De de la roue.This distance is equal to 59% of the outside diameter De of the wheel.

La roue est du type à aubes crochantes, dont le diamètre interne est compris entre 70 et 80% de son diamètre extérieur, et chaque aube présente, en fonction du diamètre extérieur De de la roue, un rayon de courbure compris entre 10 et 15%, une corde comprise entre 10 et 15% et un allongement compris entre 1 et 5.The wheel is of the type with sharp blades, the internal diameter of which is between 70 and 80% of its external diameter, and each blade has, depending on the external diameter De of the wheel, a radius of curvature of between 10 and 15% , a rope between 10 and 15% and an elongation between 1 and 5.

Les aubes sont vrillées longitudinalement d'un angle d'hélice inférieur à 10°.The blades are twisted longitudinally with a helix angle of less than 10 °.

La roue est vrillée par rotation des flasques d'extrémité l'un par rapport à l'autre.The wheel is twisted by rotation of the end plates relative to one another.

L'élément de bec de crosse est vrillé d'un angle d'hélice inférieur à 10°.The butt end element is twisted with a helix angle of less than 10 °.

Un résultat de la présente invention réside dans l'obtention d'un rendement élevé qui atteint 70 à 80%.A result of the present invention lies in obtaining a high yield which reaches 70 to 80%.

Un autre résultat réside dans la mise à profit des caractéristiques intrinsèques du ventilateur transverse pour l'obtention d'un flux en nappe ou d'un rideau d'air; le débit étant de ce fait proportionnel à la longueur de la roue, à vitesse de rotation constante, on conserve la valeur des coefficients aérauliques réduits.Another result lies in taking advantage of the intrinsic characteristics of the transverse fan to obtain a sheet flow or an air curtain; the flow rate being therefore proportional to the length of the wheel, at constant speed, the value of the reduced aeraulic coefficients is kept.

Un autre résultat réside dans l'accroissement de la marge au pompage.Another result is the increase in the pumping margin.

Un autre résultat réside dans l'accessibilité à des puissances de l'ordre du mégawatt, tout en conservant un encombrement minimal comparé à celui des machines classiques de même puissance.Another result lies in the accessibility to powers of the order of megawatts, while retaining a minimum size compared to that of conventional machines of the same power.

On sait que les caractéristiques d'un ventilateur sont usuellement définies par les coefficients sans dimension de débit Cd, de pression Cp et de rendement η selon les relations:

Figure imgb0001
où L est la longueur de la roue (m), ω la vitesse de rotation de la roue (rd/s), R le rayon de la roue, ρ la masse volumique de l'air (Kg/m³), Qv le débit du ventilateur (m³/s) et Δ P la variation de pression (Pa).We know that the characteristics of a fan are usually defined by the dimensionless coefficients of flow Cd, pressure Cp and efficiency η according to the relationships:
Figure imgb0001
 where L is the length of the wheel (m), ω the speed of rotation of the wheel (rd / s), R the radius of the wheel, ρ the density of the air (Kg / m³), Qv the flow of the fan (m³ / s) and Δ P the pressure variation (Pa).

L'invention sera mieux comprise à la lecture du complément de description qui va suivre d'un mode de réalisation donné à titre indicatif en relation avec un dessin sur lequel

  • la figure 1 est une vue générale du montage d'un ventilateur transverse,
  • la figure 2 est une illustration schématique de la position du bec amont de l'élément de crosse,
  • la figure 3 est une illustration schématique de la face roue-crosse plane et la figure 4 celle de la face roue-crosse creuse,
  • la figure 5 est une illustration de la face amont plane de crosse et la figure 6 celle de la face amont creuse de crosse,
  • la figure 7 est une illustration schématique de la position du bec de volute et de la face amont de bec de volute,
  • la figure 8 illustre le tracé de la volute aval,
  • la figure 9 illustre la réalisation d'une aube de la roue,
  • la figure 10 représente une réalisation particulière de la roue,
  • la figure 11 illustre un exemple de courbes aérauliques obtenues selon l'invention.
The invention will be better understood on reading the additional description which follows of an embodiment given for information only in relation to a drawing in which
  • FIG. 1 is a general view of the mounting of a transverse fan,
  • FIG. 2 is a diagrammatic illustration of the position of the upstream spout of the stock element,
  • FIG. 3 is a schematic illustration of the flat wheel-stock face and FIG. 4 that of the hollow wheel-stock face,
  • FIG. 5 is an illustration of the planar upstream face of the butt and FIG. 6 that of the hollow upstream face of the butt,
  • FIG. 7 is a schematic illustration of the position of the volute beak and of the upstream face of the volute beak,
  • FIG. 8 illustrates the layout of the downstream volute,
  • FIG. 9 illustrates the production of a blade of the wheel,
  • FIG. 10 represents a particular embodiment of the wheel,
  • FIG. 11 illustrates an example of aeraulic curves obtained according to the invention.

Sur la figure 1, on a représenté un exemple de réalisation d'un ventilateur transverse comportant une roue 1, tournant dans le sens de la flèche F, un élément de crosse 2 et un élément de volute 3. Les éléments de volute et de crosse constituent le stator de la machine tournante et délimitent une partie amont de section convergente et une partie aval 4a de section divergente, cette dernière étant suivie d'un circuit d'utilisation 4b partiellement représenté.In Figure 1, there is shown an embodiment of a transverse fan comprising a wheel 1, rotating in the direction of the arrow F, a stock member 2 and a scroll element 3. The scroll and butt elements constitute the stator of the rotary machine and delimit an upstream part of converging section and a downstream part 4a of diverging section, the latter being followed by a use circuit 4b partially shown.

L'élément de crosse 2 comprend une face amont 5 ou volute amont, un bec amont 6, une face roue-crosse 7, un bec aval 8 et une face aval 9.The stock element 2 comprises an upstream face 5 or upstream volute, an upstream spout 6, a wheel-stock face 7, a spout downstream 8 and a downstream face 9.

L'élément de volute 3 comprend une face amont 10, un bec de volute 11 et une volute aval 12.The scroll element 3 comprises an upstream face 10, a scroll beak 11 and a downstream scroll 12.

Le bec amont 6 de crosse est placé à une distance de la roue 1 appelée entrefer 13 de bec de crosse (ECR). Le bec 11 de volute est également placé à une distance de la roue 1 appelée entrefer 14 de bec de volute (EVR).The upstream butt 6 of the butt is placed at a distance from the wheel 1 called the butt 13 of the butt (ECR). The volute nozzle 11 is also placed at a distance from the wheel 1 called volute nozzle air gap 14 (EVR).

Pour définir les caractéristiques du ventilateur selon l'invention, on se donne un repère d'axes perpendiculaires OXY dont l'origine O coincide avec l'axe de la roue 1 et dont l'axe des abscisses est parallèle à la face aval 9 de l'élément de crosse. Les dimensions linéaires sont exprimées classiquement en pourcentage du diamètre extérieur De de la roue 1.To define the characteristics of the ventilator according to the invention, a reference is given to perpendicular axes OXY whose origin O coincides with the axis of the wheel 1 and whose abscissa axis is parallel to the downstream face 9 of the butt stock. The linear dimensions are conventionally expressed as a percentage of the outside diameter De of the wheel 1.

La position du bec amont 6 de crosse est défini, conformément à la figure 2, par l'angle ABCAM entre l'axe X et le rayon D de la roue 1 passant par ce bec. Cet angle peut être compris entre 290 et 330°. On peut par construction adopter une valeur fixe de cet angle, la position des autres éléments étant définie à partir de cette valeur. Sur la figure 2, cet angle est de 309° à entrefer nul.The position of the upstream spout 6 of the butt is defined, in accordance with FIG. 2, by the angle A BCAM between the axis X and the radius D of the wheel 1 passing through this spout. This angle can be between 290 and 330 °. By construction, we can adopt a fixed value of this angle, the position of the other elements being defined from this value. In Figure 2, this angle is 309 ° with zero air gap.

La dimension de l'entrefer 13 (ECR) est comprise entre 2 et 8% du diamètre extérieur De de la roue et plus particulièrement entre 2 et 3%.The dimension of the air gap 13 (ECR) is between 2 and 8% of the outside diameter De of the wheel and more particularly between 2 and 3%.

Sur la figure 3, on a schématisé à entrefer ECR nul l'épaisseur Ec de la crosse et son inclinaison AFRC par rapport à la parallèle 15 à l'axe Y passant par le bec amont 6 de crosse. L'épaisseur Ec est comptée entre la face aval 9 plane et le plan 16 parallèle à cette face passant par le bec 6. L'épaisseur Ec est comprise entre 0,1 et 40% du diamètre extérieur De de la roue 1 et avantageusement entre 14 et 18%.In FIG. 3, the thickness Ec of the stock and its inclination A FRC with respect to the parallel 15 to the axis Y passing through the upstream nozzle 6 of the stock has been shown diagrammatically as the gap ECR zero. The thickness Ec is counted between the planar downstream face 9 and the plane 16 parallel to this face passing through the spout 6. The thickness Ec is between 0.1 and 40% of the external diameter De of the wheel 1 and advantageously between 14 and 18%.

Cette épaisseur Ec étant définie, la face 7 crosse-roue peut être soit plane, soit creuse, afin d'organiser l'écoulement interne de l'air en fonction de l'application envisagée. De même, la face crosse-roue 7a, représentée sur la figure 3, est plane et calée d'un angle AFRC, par rapport à la parallèle 15, compris entre _30 et +60° et plus particulièrement entre _10 et +10°. Par contre, la face crosse-roue 7b, représentée sur la figure 4, est creuse, en arc de cercle, le bec amont 6 et le bec aval 8 de crosse étant dans cette configuration alignés sur la parallèle 17 à l'axe Y. Le centre B de courbure de cet arc de cercle est situé sur la médiatrice de la corde 18 joignant les becs 6 et 8 et l'angle AFRC est déterminé par la tangente 19 passant par le bec 6 et la corde 18. Cet angle est compris entre 0 et 60° et avantageusement entre 10 et 25°. A noter que lorsque l'angle AFRC est nul, la face 7b est plane.This thickness Ec being defined, the face 7 of the wheel-stock can be either flat or hollow, in order to organize the internal flow of air as a function of the envisaged application. Likewise, the butt-wheel face 7a, shown in FIG. 3, is flat and wedged at an angle A FRC , with respect to the parallel 15, between _30 and + 60 ° and more particularly between _10 and + 10 °. On the other hand, the butt-wheel face 7b, represented in FIG. 4, is hollow, in an arc of a circle, the upstream spout 6 and the downstream spout 8 of the butt being in this configuration aligned on the parallel 17 to the axis Y. The center B of curvature of this arc of circle is located on the perpendicular bisector of the cord 18 joining the beaks 6 and 8 and the angle A FRC is determined by the tangent 19 passing through the beak 6 and the cord 18. This angle is between 0 and 60 ° and advantageously between 10 and 25 °. Note that when the angle A FRC is zero, the face 7b is plane.

La face amont 5 de crosse peut être soit plane 5a (figure 5) soit creuse 5b (figure 6). Elle s'étend entre le bec amont 6 de crosse et un point MFAC. La face 5a est définie par sa position angulaire par rapport à l'axe X et par sa longueur projetée sur ce même axe. L'angle AFAC est compris entre 25 et 80° et sa longueur (1) projetée est comprise entre 90 et 100% du diamètre extérieur De de la roue 1.The upstream face 5 of the stock can be either flat 5a (FIG. 5) or hollow 5b (FIG. 6). It extends between the upstream nozzle 6 of the butt and a point M FAC . The face 5a is defined by its angular position relative to the axis X and by its length projected on this same axis. The angle A FAC is between 25 and 80 ° and its projected length (1) is between 90 and 100% of the outside diameter De of the wheel 1.

La face creuse 5b, représentée sur la figure 6, est définie par l'angle A′FAC entre le rayon de la roue passant par le bec amont 6 de crosse et la tangente en ce point à la forme étudiée. L'angle A′FAC est compris comme précédemment entre 25 et 80° et plus particulièrement entre 60 et 78°. Le centre C de courbure est situé sur la médiatrice à la corde 20 passant le bec 6 et le point MFAC. La longueur (1) de la face creuse projetée sur un axe parallèle à l'axe X est comprise entre 90 et 100% du diamètre extérieur De de la roue 1.The hollow face 5b, represented in FIG. 6, is defined by the angle A ′ FAC between the radius of the wheel passing through the upstream nozzle 6 of the stock and the tangent at this point to the shape studied. The angle A ′ FAC is between 25 and 80 ° as above and more particularly between 60 and 78 °. The center C of curvature is located on the perpendicular bisector of the cord 20 passing the beak 6 and the point M FAC . The length (1) of the hollow face projected on an axis parallel to the axis X is between 90 and 100% of the external diameter De of the wheel 1.

Le bec 11 de volute, dont la position est schématisée sur la figure 7, est situé sur un arc de cercle 21, à une distance ou entrefer 14 (EVR) comprise entre 2 et 8% du diamètre extérieur De de la roue 1. L'arc de cercle 21 est délimité par l'angle ABC compris entre 76 et 112°. Sur cette figure, on voit également la face amont 10 du bec de volute incliné de l'angle AFABV par rapport au rayon passant par le bec 11 de volute. L'angle AFABV est compris entre 0 et 70°. Ces deux angles sont choisis de façon à assurer une alimentation optimale compatible avec le point nominal recherché.The volute beak 11, the position of which is shown diagrammatically in FIG. 7, is located on a circular arc 21, at a distance or air gap 14 (EVR) of between 2 and 8% of the external diameter De of the wheel 1. L 'arc of a circle 21 is delimited by the angle A BC between 76 and 112 °. This figure also shows the upstream face 10 of the volute beak inclined by the angle A FABV relative to the radius passing through the volute beak 11. The angle A FABV is between 0 and 70 °. These two angles are chosen so as to ensure an optimal supply compatible with the nominal point sought.

La figure 8 représente la volute aval 12 qui est constituée de trois parties 21, 22 et 23. La partie 21 est un arc toujours concentrique à la roue 1 et existe lorsque l'angle ABC est inférieur à 112°. Les deux parties 22 et 23 sont définies à partir de l'élément de crosse 2 en délimitant une première section notée SHBCAV (section horizontale de bec de crosse aval) parallèle à l'axe X, telle que sa longueur soit comprise entre 80 et 100% du diamètre extérieur De de la roue 1, et une seconde section notée SBCAV (section verticale de bec de crosse aval), telle que sa longueur soit comprise entre 60 et 90% du diamètre De extérieur de la roue 1. Ces sections définissent les deux points MHBCAV et MVBCAV. La volute est alors constituée par la partie 22 en arc de cercle passant par le point MHBCAV tangent à la partie 21 et à la partie plane 23 passant par le point MVBCAV et faisant un angle de 7° avec l'axe X.FIG. 8 represents the downstream volute 12 which is consisting of three parts 21, 22 and 23. Part 21 is an arc always concentric with the wheel 1 and exists when the angle A BC is less than 112 °. The two parts 22 and 23 are defined from the stock element 2 by delimiting a first section denoted SHBCAV (horizontal section of downstream stock tip) parallel to the axis X, such that its length is between 80 and 100 % of the outside diameter De of the wheel 1, and a second section denoted SBCAV (vertical section of downstream butt stock), such that its length is between 60 and 90% of the outside diameter Of the wheel 1. These sections define the colon M HBCAV and M VBCAV . The volute is then formed by the part 22 in an arc of a circle passing through the point M HBCAV tangent to the part 21 and the flat part 23 passing through the point M VBCAV and making an angle of 7 ° with the axis X.

La volute est enfin reliée au plan divergent 24 par la partie plane 23 prolongeant ce dernier. Le divergent 4b est délimité par une surface plane prolongeant la face aval 9 de crosse et la partie plane 24 faisant un angle de 7° avec l'axe X. Ceci conduit à un divergent de ventilateur à 7°, valeur communément admise en mécanique des fluides pour ce qui concerne l'obtention d'une perte de charge minimale.The volute is finally connected to the divergent plane 24 by the planar part 23 extending the latter. The divergent 4b is delimited by a flat surface extending the downstream face 9 of the butt and the flat part 24 making an angle of 7 ° with the axis X. This leads to a fan divergent at 7 °, a value commonly accepted in mechanical mechanics. fluids with regard to obtaining a minimum pressure drop.

La roue d'un ventilateur transverse est définie de façon connue par les paramètres suivants: diamètres extérieur et intérieur, longueur, nombre de pales, rayon de courbure de la pale, corde de la pale, angles d'entrée et de sortie de la pale, diamètre de flasque. Les plages de variation de ces paramètres sont bien connues et il n'est pas nécessaire de les expliciter en détail.The wheel of a transverse fan is defined in a known manner by the following parameters: outside and inside diameters, length, number of blades, radius of curvature of the blade, chord of the blade, angles of entry and exit of the blade , flange diameter. The ranges of variation of these parameters are well known and it is not necessary to explain them in detail.

Par simplification, on a représenté sur la figure 9 une aube 25 de la roue 1 qui est du type crochante, c'est-à-dire quand β₁₁ est supérieur à 90°. Chaque aube est définie par les paramètres suivants:

  • le rapport du diamètre interne Di et du diamètre externe De de la roue; ce rapport est usuellement compris entre 0,7 et 0,8;
  • le rayon de courbure R; il est compris entre 10 et 15% du diamètre extérieur De de la roue,
  • la corde C; elle est comprise entre 10 et 15% du diamètre extérieur De de la roue,
  • l'allongement; il est exprimé par le rapport longueur/diamètre et varie entre 1 et 5.
For simplification, there is shown in Figure 9 a blade 25 of the wheel 1 which is of the spitting type, that is to say when β₁₁ is greater than 90 °. Each blade is defined by the following parameters:
  • the ratio of the internal diameter Di and the external diameter De of the wheel; this ratio is usually between 0.7 and 0.8;
  • the radius of curvature R; it is between 10 and 15% of the outside diameter De of the wheel,
  • rope C; it is between 10 and 15% of the outside diameter De of the wheel,
  • elongation; it is expressed by the length / diameter ratio and varies between 1 and 5.

Ces paramètres permettent de caler l'aube et de définir les angles β₁₁ et β₁₂ qui varient respectivement dans la fourchette 120 à 170° et 70 à 100°.These parameters make it possible to set the dawn and define the angles β₁₁ and β₁₂ which vary respectively in the range 120 to 170 ° and 70 to 100 °.

La roue 1 peut être vrillée comme représenté sur la figure 10 par rotation des flasques 26 et 27 l'un par rapport à l'autre d'un angle d'hélice AH. Le bord d'attaque 28 de chaque aube 25 définit alors une courbe présentant un angle d'hélice AH inférieur à 10°. Cette réalisation permet entre autres de diminuer le bruit et l'amplitude des vibrations. En variante, la ligne décrite par le bec 11 de volute et/ou le bec amont 6 de crosse peuvent être vrillés suivant la même loi.The wheel 1 can be twisted as shown in FIG. 10 by rotation of the flanges 26 and 27 relative to each other by a helix angle A H. The leading edge 28 of each blade 25 then defines a curve having a helix angle A H less than 10 °. This achievement makes it possible, among other things, to reduce the noise and the amplitude of the vibrations. Alternatively, the line described by the volute beak 11 and / or the upstream beak 6 of the butt can be twisted according to the same law.

Sur la figure 11, on a représenté la caractéristique pression/débit d'un ventilateur transverse ayant les caractéristiques géométriques suivantes:
diamètre extérieur De = 283 mm
diamètre intérieur Di = 223 mm soit Di/De = 78,95%
nombre d'aubages Np = 40
Crosse droite EC = 46 mm soit EC/De = 16,25%
AFRC = 0°
AFAC à entrefer mini = 40°
Rayon de courbure de la volute amont de crosse = 251 mm
AFABV à entrefer mini = 40°
SHBCAV à entrefer mini = 166 mm soit 58,64% de De
SVBCAV à entrefer mini = 220 mm soit 77,73% de De
Rayon de courbure de la volute aval = 301 mm soit 106,47% de De
Entrefer volute/roue EVR = 6 mm soit 2,12% de De
Entrefer crosse/roue ECR = 8 mm soit 3,03% de De.
La puissance obtenue est d'environ 2 KWatt pour un ventilateur de 420 mm de longueur, alors que l'obtention d'une puissance équivalente à l'aide d'un ventilateur axial ou centrifuge nécessiterait un diamètre et une longueur d'au moins 2 à 3 fois plus grands. Les valeurs Δ P et Qv sont mesurées à la sortie du ventilateur. La courbe P représente la variation de pression et la courbe R le rendement.FIG. 11 shows the pressure / flow characteristic of a transverse fan having the following geometric characteristics:
outer diameter D e = 283 mm
inner diameter D i = 223 mm i.e. D i / D e = 78.95%
number of blades Np = 40
Straight stock E C = 46 mm i.e. E C / De = 16.25%
A FRC = 0 °
A FAC with minimum air gap = 40 °
Radius of curvature of the upstream stock volute = 251 mm
A FABV with minimum air gap = 40 °
S HBCAV with minimum air gap = 166 mm or 58.64% of De
S VBCAV with minimum air gap = 220 mm or 77.73% of De
Radius of curvature of the downstream volute = 301 mm or 106.47% of De
Volute / EVR air gap = 6 mm or 2.12% of De
Stock air gap / ECR wheel = 8 mm or 3.03% of De.
The power obtained is approximately 2 KWatt for a fan 420 mm long, while obtaining a power equivalent using an axial or centrifugal fan would require a diameter and a length of at least 2 to 3 times larger. The Δ P and Qv values are measured at the fan outlet. Curve P represents the pressure variation and curve R the efficiency.

On constate qu'on obtient simultanément de forts maxima de pression de l'ordre de 750 Pa pour de forts débits de l'ordre de 2 m³/s et ce pour un rendement utilisable de l'ordre de 60%. En outre, ce ventilateur dispose d'une marge au pompage Δ Q accrue, comparativement aux machines classiques à courbe bossue et peut être utilisé dans une plage d'excursion en débit exempte de risques de pompage. Sur cette figure, on voit que cette marge Δ Q est de l'ordre de 1 m³/s. Ce type de ventilateur peut donc être utilisé notamment dans la sustentation des navires à effet de surface.It can be seen that high pressure maxima of the order of 750 Pa are obtained simultaneously for high flow rates of the order of 2 m³ / s and this for a usable yield of the order of 60%. In addition, this fan has an increased pumping margin Δ Q compared to conventional machines with a hunchback curve and can be used in a range of flow excursion free of pumping risks. In this figure, it can be seen that this margin Δ Q is of the order of 1 m³ / s. This type of ventilator can therefore be used in particular in the lifting of surface effect vessels.

Claims (17)

1. Cross flow fan comprising an convergent inlet demarcated by upstream face (10) of scroll element (3) and upstream face (5) of cross-head element (2), impeller (1) or rotor provided with blades and divergent (4a) demarcated by downstream face (12) of scroll element and downstream face (9) of cross-head element, said inlet and said divergent demarcating with respect to the impeller in a plane perpendicular to its axis of rotation two narrowing longitudinal passages (13, 14) defined on the one hand by leading edge (1) of scroll element and on the other hand by upstream leading edge (6) of cross-head element (2), wherein in a reference system of perpendicular axes X and Y, whose origin is placed at the axis of rotation of impeller (1), and whose abscissas axis X is parallel to downstream face (9) of the cross-head element, it features:
- an upstream leading edge (6) of cross-head element describing an angle ABCAM included between 290 and 330° at a distance from impeller or air gap (13) included between 2 and 8% of outside diameter De of the impeller,
- a face (7) of cross-head element describing an angle AFRC whose apex is one and the same as upstream leading edge (6) of cross-head included between _20° and 60° with respect to an axis (15) parallel to the ordinates axis concurrent with upstream axis (6),
- a scroll leading edge (11) describing an angle ABV included between 76 and 112° at a distance from impeller or air gap (14) included between 2 and 8% of outside diameter De of the impeller,
- a plane upstream face (10), concurrent with leading edge (11) of scroll, inclined with respect to the plane connecting the axis of rotation of the impeller and the scroll leading edge (11) by an angle AFABV of a value included between 0 and 70°.
2. Fan according to claim 1, wherein said cross-head element (2) presents between its upstream leading edge (6) and downstream leading edge (8) a thickness included between 1 and 40% of the outside diameter De of the impeller.
3. Fan according to claim 2, wherein the thickness Ec of the cross-head element (2) is equal to 16.25% of outside diameter De of the impeller.
4. Fan according to claim 3, wherein said cross-head-impeller face (7) is plane and inclined with respect to the Y axis by an angle AFAC included between _20 and 60°.
5. Fan according to claim 3, wherein said cross-head/impeller face (7) is hollow and in the form of a circle arc (7b) passing through upstream (6) and dowstream leading edge (8) of cross-head element both placed on a line parrallel to axis Y such that tangent (19) to upstream leading edge (6) demarcates an angle AFRC with said parallel to axis Y such that O < AFRC ≦ 60°.
6. Fan according to claim 5, wherein the length (1) of upstream face (5) of the cross-head, projected onto the X axis is included between 90 and 100% of outside diameter De of the impeller.
7. Fan according to claim 6, wherein said upstream face (5) of the cross-head comprises a plane surface inclined by an angle AFAC included between 10 and 30° with respect to the X axis.
8. Fan according to claim 7, wherein said angle of inclination equals 26° and the length (1) equals 95% of outside diameter De of the impeller.
9. Fan according to claim 6, wherein said upstream face (5) of cross-head comprises a circle arc (5) open toward the impeller whose tangent to upstream leading edge (6) of the cross-head, demarcates with respect to a radius passing through upstream leading edge (6) an angle AFAC included between 20 and 80°.
10. Fan according to claim 1, wherein said downstream scroll (12) extends in a divergent (24) demarcating an angle of 7° with respect to the abscissa axis from a point located on a parallel to the ordinate axis passing through the downstream cross-head leading edge at a distance from said leading edge included between 60 and 90% of outside diameter De of the impeller.
11. Fan according to claim 10, wherein said downstream scroll (12) is demarcated in its section by a first circle arc (21) concentric with impeller (1) and a second circle arc (22) connecting the first circle arc to divergent (24).
12. Fan according to claim 11, wherein said downstream scroll (3) passes through an axis placed on a line parallel to the X axis passing through downstream leading edge (8) of cross-head (2), at a distance from the latter included between 60 and 120% of outside diameter De of the impeller.
13. Fan according to claim 12, wherein said distance equals 59% of the outside diameter of the impeller.
14. Fan according to claim 13, wherein said impeller is of forward-curved blade type with an internal diameter included between 70 and 80% of its outside diameter and in that each blade has, as a function of outside diameter De of the impeller, a curve radius included between 10 and 15%, a chord of between 10 and 15% and an aspect ration included between 1 and 5.
15. Fan according to claim 14, wherein said blades (25) are longitudinally twisted through an angle of helix AH less than 10°.
16. Fan according to claim 15, wherein said impeller (51) is twisted by the rotation of end flanges (26, 27) with respect to one another.
17. Fan according to claim 15, wherein said cross-head leading edge element (2) is twisted through an angle of helix of less than 10°.
EP88402086A 1987-08-13 1988-08-11 Cross-flow fan Expired - Lifetime EP0303543B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR8711522 1987-08-13
FR8711522A FR2619422B1 (en) 1987-08-13 1987-08-13 CROSS-CURRENT FAN

Publications (2)

Publication Number Publication Date
EP0303543A1 EP0303543A1 (en) 1989-02-15
EP0303543B1 true EP0303543B1 (en) 1991-05-08

Family

ID=9354165

Family Applications (1)

Application Number Title Priority Date Filing Date
EP88402086A Expired - Lifetime EP0303543B1 (en) 1987-08-13 1988-08-11 Cross-flow fan

Country Status (8)

Country Link
US (1) US4836743A (en)
EP (1) EP0303543B1 (en)
JP (1) JP2767747B2 (en)
CA (1) CA1337984C (en)
DE (1) DE3862709D1 (en)
ES (1) ES2023267B3 (en)
FR (1) FR2619422B1 (en)
NO (1) NO169360C (en)

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US4906219A (en) * 1988-08-15 1990-03-06 J. I. Case Company Cleaning system for a combine
KR960703203A (en) * 1994-04-28 1996-06-19 시게후치 마사토시 MULTIVANE RADIAL FAN DESIGNING METHOD AND MULTIVANE RADIAL FAN
JP3632789B2 (en) * 1995-08-28 2005-03-23 東陶機器株式会社 Multiblade centrifugal fan design method and multiblade centrifugal fan
KR0141763B1 (en) * 1995-12-19 1998-07-01 구자홍 Rear guider of cross flow blower
JP3649567B2 (en) * 1998-01-12 2005-05-18 三菱電機株式会社 Once-through fan
US6146092A (en) * 1998-07-13 2000-11-14 Ford Motor Company Centrifugal blower assembly with a diffuser
US6261051B1 (en) * 1998-09-02 2001-07-17 Gordon A. Kolacny Fan duct combination unit
KR100731366B1 (en) * 2005-11-04 2007-06-21 엘지전자 주식회사 Cooling apparatus for flat display device and cross flow fan for the same
US20120134794A1 (en) * 2009-08-25 2012-05-31 Mitsubishi Electric Corporation Fan and air-conditioning apparatus provided with fan
CN203189282U (en) * 2010-03-12 2013-09-11 沃尔纳多航空有限公司 Tower type fan
TWI479083B (en) * 2012-06-21 2015-04-01 Sunonwealth Electr Mach Ind Co Advection-type fan and a housing thereof
TWI624589B (en) * 2016-07-21 2018-05-21 Lai Rong Yi Low head large flow channel turbine

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GB757543A (en) * 1953-07-17 1956-09-19 H A Saunders Ltd Improvements relating to hand scoops incorporating weighing mechanism
GB830362A (en) * 1956-05-08 1960-03-16 Machinenfabrik Benninger A G Improvements in transverse flow blowers
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DE3326651A1 (en) * 1983-07-23 1985-01-31 Standard Elektrik Lorenz Ag, 7000 Stuttgart CROSS-FLOW FAN

Also Published As

Publication number Publication date
EP0303543A1 (en) 1989-02-15
ES2023267B3 (en) 1992-01-01
JPH01195991A (en) 1989-08-07
NO169360B (en) 1992-03-02
NO883600L (en) 1989-02-14
FR2619422B1 (en) 1989-12-08
JP2767747B2 (en) 1998-06-18
FR2619422A1 (en) 1989-02-17
CA1337984C (en) 1996-01-23
US4836743A (en) 1989-06-06
DE3862709D1 (en) 1991-06-13
NO169360C (en) 1992-06-10
NO883600D0 (en) 1988-08-12

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