EP4317698A1 - Ventilateur à flux transversal, ventilo-convecteur comprenant ledit ventilateur et procédé de réglage dudit ventilo-convecteur - Google Patents

Ventilateur à flux transversal, ventilo-convecteur comprenant ledit ventilateur et procédé de réglage dudit ventilo-convecteur Download PDF

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Publication number
EP4317698A1
EP4317698A1 EP23188586.4A EP23188586A EP4317698A1 EP 4317698 A1 EP4317698 A1 EP 4317698A1 EP 23188586 A EP23188586 A EP 23188586A EP 4317698 A1 EP4317698 A1 EP 4317698A1
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EP
European Patent Office
Prior art keywords
impeller
fan
air
axis
arg
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Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
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EP23188586.4A
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German (de)
English (en)
Inventor
Vittorio RUFFINI
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Ideal Clima Srl
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Ideal Clima Srl
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Publication date
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Publication of EP4317698A1 publication Critical patent/EP4317698A1/fr
Pending legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/4206—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps
    • F04D29/422—Discharge tongues
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/4206—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps
    • F04D29/4226—Fan casings

Definitions

  • the present invention relates to a fan of the cross-flow type, a fan coil comprising said fan and a process for setting up said fan coil.
  • Said fan and fan coil are particularly suitable to be set up for example in houses, offices, shops, malls, museums, libraries, or other environments in which a particular noiselessness and a pleasant aesthetics are required.
  • the cross-flow type fans are characterized by comprising an impeller formed by a substantially cylindrical bundle of blades having the form of plates which upon rotating is crossed from side to side by an air flow overall perpendicular or transverse to the axis of rotation of the impeller itself.
  • the diffusion in the field of air conditioning is due to its compactness, operation noiselessness, and attitude to be made as an impeller/casing assembly with a two-dimensional form which can be extruded according to an axis for the length suitable to generate the required flow rate.
  • cross-flow fans manage to be enough noiseless to be set up in air conditioning systems for houses and offices only if the directions of the air delivery and intake form a remarkably accentuated elbow, which usually forms an angle of about 90 °, while when the air delivery and intake are substantially aligned, i.e., when they are substantially coaxial, are so noisy and inefficient to be absent from the market. Axial fans are equally noisy.
  • the fan coils comprising cross-flow fans should currently have a front air intake, turned towards the centre of the room in which they are set up and well visible, with its typical grid, to an observer.
  • the air intake is desired to be arranged on the rear face of the fan coil, this should be arranged at enough distance from the back wall, of about a dozen centimetres which, if summed to the thickness of the fan coil itself, would lead it to excessively protrude in the environment in which it is set up, resulting hindering and quite ugly looking.
  • a model in scale 1:1 of the fan of Figure 1 was shown to be excessively noisy and too much low in performance to be used in a fan coil.
  • An object of the present invention is to overcome the above-mentioned drawbacks and particularly to provide a cross-flow type fan with substantially aligned axes of the air delivery and intake which is less noisy and more efficient than the known in-line cross-flow fans and thus more suitable to be mounted for example in a fan coil.
  • said object is achieved by a fan having the features according to claim 1.
  • said object is achieved by a fan coil having the features according to claim 15.
  • said object is achieved by a process for setting up a fan coil having the features according to claim 16.
  • Figures 6-13 relate to a cross-flow type fan according to a first particular embodiment of the invention, referred to by overall reference 1.
  • the fan 1 comprises a casing 3 and an impeller 5 arranged in the casing 3 ( Figure 7 ).
  • the casing 3 is preferably a substantially rigid shell, made of metal or plastic material.
  • the impeller 5 is of the cross-flow type.
  • the impeller 5 comprises a substantially cylindrical bundle of blades 52 arranged with their axes substantially parallel or otherwise longitudinal to the axis of rotation ARG of the impeller 5.
  • the cylindrical bundle formed by the assembly of the blades 52 is preferably a circular section cylinder ( Figure 12 ).
  • the blades 52 have the concavity preferably turned in a direction concordant with their advancing direction and with the rotation way of the impeller 5 ( Figure 12 ).
  • the fan 1 preferably comprises a motor 6, for example of the brushless type or other electric motor, for driving the impeller 5 by rotating it around the axis ARG ( Figure 6 )
  • the casing 3 forms:
  • the air intake 7, which can be for example an opening in the casing 3, comprising or not grids, feeds with the air the intake duct 8 ( Figure 7 ).
  • the casing 3 can substantially have the form of a solid obtained by extruding a two-dimensional form along an axis of extrusion parallel to the axis of rotation ARG of the impeller ( Figure 12 ).
  • the delivery duct 10 feeds with the air the delivery vent 9 and/or the delivery duct 10 ( Figure 7 ).
  • the impeller 5 is configured for rotating on itself around an axis of rotation ARG so as to blow the air coming from the air intake 7 towards the delivery vent 9.
  • the impeller 5 forms flanks 50 that extend parallel or otherwise longitudinally to and around the impeller axis of rotation ARG ( Figure 6 ).
  • the fan 1 is configured so that at least part - and preferably at least most - of the air coming from the air intake 7 and/or from the intake duct 8 enters the fan 5 through a first zone 501 of its flanks 50, conventionally referred to as upstream zone of the flanks 501 and located at or otherwise in proximity to the air intake 7 and/or the intake duct 8, crosses the impeller 5 flowing in a direction DCROSS overall perpendicular or otherwise transverse to the axis of rotation ARG and outflows at least in part - preferably for most - through a second zone 503 of its flanks 50 at or otherwise in proximity to the air delivery vent 9 and/or the delivery duct 10, i.e., through the so called downstream zone of the flanks 503.
  • first 501 and the second zone 503 of the flanks 50 are substantially diametrically opposed to each other with respect to the centre or axis of rotation ARG ( Figure 7 , 12 ) .
  • the fan 1 is configured so that part of the air that crosses the impeller 5 forms a main vortex VPR, flows out of the downstream zone of the flanks 503, flowing into a space - i.e., into the stabilising cavity 30 - between the flanks of the impeller 50 and the casing returns into a third zone 505 of the flanks 50 of the impeller, said vortex inlet zone 505, having an angular position between the upstream zone of the flanks 501 and the downstream zone of the flanks 503 ( Figure 7 , 12 ).
  • the upstream zone of the flanks 501, the downstream zone of the flanks 503 and the vortex inlet zone 505 can have the form of sectors of a cylindrical or revolution surface, respectively.
  • the casing 3 forms, on its side facing or otherwise turned towards the portion of the impeller 5 whose blades 52 move away from the delivery vent 9 and/or from the delivery duct 10 and approach the air intake 7 and/or the intake duct 8, a stabilising cavity 30 which is configured for accommodating and guiding the main vortex VPR outside the impeller 5.
  • the stabilising cavity 30 extends over an angular range, measured with respect to the centre or axis of rotation ARG of the impeller, comprised between -70° and +50° with respect to the reference line or plane of the angles RFA.
  • the reference line or plane of the angles RFA is respectively a line or plane passing through the centre or axis ARG of rotation of the impeller 5 and substantially perpendicular to the average direction DCROSS of the air flow that crosses the left half of the impeller 5.
  • Left half of the impeller 5 means the half of the impeller 5 in which the main vortex VPR does not lie ( Figure 8 ).
  • the left and right halves of the impeller 5 are separated by an ideal plane or line passing through the centre or axis of rotation ARG and perpendicular to the line RFA ( Figure 8 ).
  • the above-mentioned average speed of the air in the left half of the impeller can also be an instantaneous speed over time but averaged in the space, considering the unweighted - vectorial integral or sum - average of the instantaneous speeds of the air in any point of the left half of the impeller 5.
  • the direction DCROSS is preferably determined only by the form of the parts of the casing 3 outside the impeller, by the form of the blades 52 and by the speed of rotation of the impeller.
  • the stabilising cavity 30 is advantageously delimited by an attachment edge 32 which is configured for separating the air flow of the main vortex from the air flow directed towards the delivery vent 9 and/or towards the delivery duct 10.
  • the attachment edge 32 is at a radial distance DRB from the axis of rotation ARG of the impeller equal to or greater than 1.2 times the radius of the impeller 5.
  • the stabilising cavity 30 extends over an angular range comprised between -60° and +40°, and more preferably comprised between -50° and +30° or between -45° and +20° with respect to the reference line or plane of the angles RFA.
  • the radial distance DRB is equal to or greater than 1.3 times the radius of the impeller 5, and even more preferably is equal to or greater than 1.4 times or 1.5 times the radius of the impeller 5.
  • the radial distance DRB is equal to or smaller than 2 times, and more preferably equal to or lower than 1.7 times, 1.6 times or 1.5 times the radius of the impeller 5.
  • the attachment edge 32 is arranged in an angular position comprised between 0° and +50°, or between 0° and +40°, between +5° and +30°, between +10° and +20° or between +18° and +22° with respect to the reference line or plane of the angles RFA.
  • the stabilising cavity 30 is preferably further delimited by an outlet edge 34 that separates the cavity 30 from the air intake 7 or the intake duct 8.
  • the outlet edge is preferably the last part of the stabilising cavity 30 which the main vortex skims before returning in the flanks of the impeller 5.
  • the outlet edge 34 is preferably configured for diverting the flow of the main vortex VPS from the outside towards the inside of the impeller 5.
  • the distance DRP initially increases, reaches a maximum value DRP_max and then preferably continuously decreases even if not necessarily at a uniform speed as the angular position ⁇ varies.
  • the value DRP_max is advantageously comprised between 1.3-2 times the radius of the impeller 5, and more preferably is comprised between 1.4-1.8 times, between 1.5-1.6 times or between 1.55-1.56 times the radius of the impeller 5.
  • the value DRP_max is reached in an angular position ⁇ advantageously comprised between -10° and 20°, and more preferably comprised between 0° and +15°, between +5° and +15°, between +7° and +13° or between +10° and +11°.
  • the attachment edge 32 and the point of the inner wall 31 to which the maximum value DRP_max corresponds can be connected by a first wide wall 33 substantially plane ( Figure 7A ).
  • outlet edge 34 and the point of the inner wall 31 to which the maximum value DRP_max corresponds can be connected by a second wide wall 35 substantially plane ( Figure 7 ).
  • the attachment edge 32, the point of the inner wall 31 to which the maximum value DRP_max corresponds and the outlet edge 34 can be connected to each other by an overall curved wall, for example having a concavity turned towards the axis ARG or otherwise towards the inside of the impeller 5.
  • the cross sections of the attachment edge 32 form a wedge having a top angle ⁇ 1 [ theta1 ] preferably comprised between 20°-80°, and more preferably comprised between 30°-70°, between 60°-70° or between 63°-67°.
  • the substantially plane walls 33, 35 can have a reciprocal tilt ⁇ 2 [theta 2 ] comprised between 90°-130° and more preferably between 100°-110°.
  • the cross sections of the attachment edge 32, the outlet edge 34 and the inlet edge 38 substantially have the form of cusps, claws, sickles, or substantially radial protrusions ( Figure 7 ).
  • the attachment edge 32 and/or the outlet edge 34 is interposed between two adjacent zones of the casing 3 in which the inner walls of the casing 3 itself are at radial distances DRP from the axis of rotation ARG of the impeller 5 substantially greater than the minimum radial distance of the attachment edge 32 and/or the outlet edge 34 from the axis of rotation ARG.
  • the radial distance DRP of the points of the inner wall 31 decreases relatively quickly, for example with an average variation ⁇ DRP [delta_ DRP ] of the radial distance DRP comprised between 0.006-0.01 times the radius of the impeller 5 for each degree of variation of the angular position ⁇ , i.e., 0.006-0.01 ⁇ DRP /degree.
  • the average variation is comprised between 0.007-0.09 ⁇ DRP/degree, between 0.0077-0.08 ⁇ DRP /degree, between 0.0077-0.0085 ⁇ DRP /degree or equal to about 0.008 ⁇ DRP /degree.
  • the radial distance of the points of the inner wall 31 decrease monotonically, in the mathematical sense of the term.
  • the distance DRP is preferably comprised between 1.03-1.2 times the radius of the impeller 5, or between 1.13-1.18 times the radius of the impeller 5.
  • the radial distance of the outlet edge 34 from the centre or axis of rotation ARG is preferably comprised between 1.03-1.2 times the radius of the impeller 5, and more preferably comprised between 1.03-1.14 times, between 1.04-1.1 times or 1.05-1.07 times the radius of the impeller 5, so as to reintroduce into the flanks 50 of the impeller as much of the flow of the main vortex as possible.
  • the space comprised between the inner walls of the stabilising cavity 30, the outer flanks 50 of the impeller 5 and the ideal straight lines joining the axis ARG respectively to the attachment 32 and outlet 34 edges has an area comprised between about 0.3-0.5 times the square of the radius of the impeller 5; said space is more preferably comprised between 0.3-0.4 times, between 0.34-0.38 times and more preferably equal to about 0.36-0.37 times the square of the radius of the impeller 5.
  • the sector of the impeller 5 facing the air intake 7 or on the downstream end of the intake duct 8 has an angular extension ⁇ 5 [theta 5 ], measured with reference to the centre or axis of rotation ARG, comprised between 90°-140° and more preferably comprised between 100°-130° , more preferably between 110°-120° and still more preferably equal to about 116°-117° ( Figure 8 ) .
  • the casing 3 forms a passage 36 immediately upstream of the impeller 5 through which the air coming from the air intake 7 and/or the intake duct 8 reaches the upstream zone of the flanks 501 of the impeller 5.
  • downstream air intake 36 coincides with the passage section more downstream of the intake duct 8 when it is present, while when it is absent, it coincides with the air intake 7.
  • the left side of the downstream air intake 36 preferably forms an inlet edge 38.
  • the right side of the downstream air intake 36 can form the outlet edge 34.
  • the downstream air intake 36 can have for example the form of a substantially rectangular opening ( Figure 7 ).
  • the inlet edge 38 has an angular position ⁇ _BI [alfa_BI] preferably comprised between 5°-40°, and more preferably comprised between 10°-30°, between 15°-25° or between 19°-21° with respect to the reference line or plane of the angles RFA ( Figure 8 ), in proximity to the left side of the impeller 5.
  • the outlet edge 34 has an angular position ⁇ _BU [alfa_BU] preferably comprised between 20°-65° , and more preferably comprised between 30°-50° , between 40°-47° or between 43°-46° with respect to the reference line or plane of the angles RFA, in proximity to the right side of the impeller 5.
  • the radial distance of the inlet edge 38 from the centre or axis of rotation ARG can be for example equal to and preferably greater - for example comprised between two and six times, or between 1.5 and four times - than that of the outlet edge 34.
  • the width of the downstream air intake 36 i.e., the distance between the inlet edge and the outlet edge 34 is preferably comprised between 1.3-2.5 times the radius of the impeller 5, and more preferably comprised between 1.5-2 times, between 1.7-1.9 or between 1.75-1.85 times the radius of the impeller 5,
  • the impeller 5 protrudes upstream through the downstream air intake 36 by a depth PRB, measured according to a radius of the impeller 5 and starting from the downstream air intake 36, preferably comprised between 0.3-0.6 times the radius of the impeller 5, and more preferably comprised between 0.4-0.5 times or 0.45-0.47 times the radius of the impeller 5.
  • inlet edge 38 and the downstream air intake 36 remarkably contribute to reduce the noisiness of the fan 1; indeed, the inlet edge 38 and the downstream air intake 36 are supposed to make the direction of the air speed in the various points inside the impeller ( Figure 12 ) more uniform and thus the air flow exiting from the impeller 5 itself more ordered and less turbulent and swirling.
  • AXPV The axis of the intake duct 8 at its most downstream end
  • AXMM The axis of the delivery duct 10 at its most upstream end
  • the axes AXPV and AXMM are tilted to each other at an angle ⁇ 6 [theta6] comprised between 120°-180°, and more preferably between 1 30°-180° or between 140°-180° so as to make a cross-flow fan with air inlet and outlet substantially aligned ( Figure 9 ).
  • the minimum distance between the axis of rotation ARG and the axes AXPV or AXMM is preferably equal to or lower than 0.8 times the radius of the impeller 5, and more preferably equal to or lower than 0.7 times or 0.65 times the radius of the impeller 5 ( Figure 9 ).
  • the minimum distance therebetween in a point inside the fan 1 is advantageously equal to or smaller than 1.5 times the radius of the impeller 5, and more preferably equal to or lower than 1 time, 0.7 times or 0.62 times the radius of the impeller 5.
  • the axis of the delivery duct 10 has an overall curved form, for example an arc or a S-form, so that the angle between the axes AXP and AXM respectively of the intake duct 8 have a relative tilt to each other progressively smaller as the distance from the axis ARG of the considered point of the ducts 8, 10 at which the tilts of the axes AXP and AXM are detected increases ( Figure 10 ).
  • one or more cross sections of the inner duct of the casing 3, according to section planes perpendicular to the axis ARG, have the form defined in points by the following Table 1 ( Figure 11 ): Point Angular position ⁇ [sexagesimal degrees] with respect to the axis or plane RFA DRP, i.e., ratio between the radial distance, of the point from the centre or axis ARG and the radius of the impeller 5 Left side A 193 1.758 1 199 1.216 2 194 1.066 3 173 1.047 4 135 1.063 5 125 1.160 6 100 1.256 7 77 1.414 8 61 1.603 9 48 1.916 10 42 2.271 B 40 2.592 Right side C 26 2.842 11 24 2.604 12 21 2.212 13 20 1.891 D 20 1.494 14 18 1.462 15 11 1.556 E 9 1.558 E1 -9 1.258 F -39 1.162 16 -41 1.139 17 -43 1.057 18 -45 1.052 G
  • the fan 1 Due to the previously described constructive measures, the fan 1, despite having the air intake 7 and the delivery vent 9 almost aligned, is much more noiseless than the known line cross-flow fans and even more noiseless than the known cross-flow fans with an elbow between the air delivery and intake, so as to be mounted in fan coils with success and satisfaction of the buyers; meanwhile, the fan 1 has much more mechanical and fluidical efficiency than the known line cross-flow fans and allows to arrange the air intake 7 of the fan coil and the fan itself on the face of the fan coil intended to be turned towards the floor or ceiling to which the fan coil is close, hiding the air intake to the view of an observer.
  • the air flows can be seen to be particularly ordered and less turbulent, the attachment edge 32 being far enough away from the flanks 50 of the impeller 5 orderly divides the air flow directed towards the delivery duct 10 from the flow of the main vortex VPR that, exited from the flanks of the impeller 5 enters the stabilising cavity 30.
  • the form of the stabilising cavity 30 and the outlet edge 34 on one hand allows the main vortex VPR to expand, on the other hand does not allow it to disperse its energy in vibrations and noise and completely reintroduces it in the flanks of the impeller 5, as the flow of the vortex VPR in the chamber 30 approaches the outlet edge 34.
  • the S-form of the delivery duct 10 also contributes to particularly orderly drive the air flow blown by the impeller 5.
  • the fan coil 100 in which the fan 1 can be set up comprises, in addition to the fan 1 itself, an air-gas heat exchanger 101 internally travelled and cooled by a gas or other cooling fluid ( Figure 11 ).
  • the exchanger 101 can have for example the overall and approximate form of a panel and is preferably arranged downstream of the delivery vent 9 and/or the delivery duct 10 of the fan 1 so as to direct the air flow produced by the impeller 5 against and possibly through the heat exchanger 101, so as to be cooled by it in a per se known manner.
  • the air intake 7 can be obtained on the lower face 102 of the fan coil 100, i.e., on the face intended to be turned towards the floor if the fan coil 100 should be set up in proximity to it or otherwise at a relatively low height, for example so that the eyes of the observers stepping on the floor are higher than the upper face 103 of the fan coil.
  • the air intake 7 can be obtained on the upper face of the fan coil 100, i.e., on the face intended to be turned towards a ceiling if the fan coil 100 should be set up in proximity to it or otherwise at a relatively large height so as not to be visible for the observers stepping on the floor below.
  • the fan coil 100 preferably further comprises an outer casing 103 containing and hiding the fan 1 and the heat exchanger 101.
  • the Applicant has made two previously described prototypes of the fan coil and tested the sound power levels thereof in a reverberation chamber according to the standard UNI EN ISO 3741:2010/ EC 1-2013.
  • the first prototype of fan coil 100 was characterized by:
  • the measured sound power levels of said first prototype are reported in the following Table 1: Number of revolutions of the impeller 5 1200 rpm 920 rpm 700 rpm 500 rpm Air flow rate [cubic metres/hour] 158 108 79 59 Pondered global sound power level A [dB] in the band 100 Hz-10.000 Hz 44.5 36.8 32.6 30.6
  • the second prototype of fan coil 100 was characterized by:
  • the measured sound power levels of said first prototype are reported in the following Table 1: Number of revolutions of the impeller 5 1200 rpm 920 rpm 700 rpm 500 rpm Air flow rate m3/h 333 242 166 91 Pondered global sound power level A [dB] in the band 100 Hz-10.000 Hz 50.6 43.2 35.1 29.2
  • the preceding sound power levels are lower by at least 3-6 dB than known fan coils having similar power, size, and air flow rate and an elbow of about 90° between the air delivery and intake.
  • the radial distance DRP of the points of the inner walls of the casing 3 can also differ even by +-30% of the values DRP indicated in Table 1.
  • the attachment 32, outlet 34 and inlet 38 edges can be substantially sharpened, sharp-edged, or even relatively bevelled, for example so that the cross sections of their vertex or apex in section planes perpendicular to the axis ARG have a minimum radius of curvature equal to or greater than a thousandth, a hundredth, a fiftieth, a thirtieth, a twentieth, or a tenth of the radius of the impeller 5.
  • said minimum radius of curvature of the attachment 32, outlet 34 and inlet 38 edges is equal to or lower than a tenth or a twentieth or a thirtieth of the radius of the impeller 5.
  • the minimum radius of curvature of the inlet edge 38 is substantially greater than the minimum radius of curvature of the attachment 32 and outlet 34 edges and is preferably equal to or greater than twice or three times the minimum radius of curvature of the attachment 32 and outlet 34 edges.
  • the minimum radius of curvature of the inlet edge 38 is comprised between 1.5-6 times, or between 2-4 times or between 2-3 times the minimum radius of curvature of the attachment 32 and outlet 34 edges.
  • the intake duct 8 can not only relatively quickly narrow ideally approaching the impeller 5 ( Figure 11 ), but also have passage sections with substantially constant area or width ( Figure 14 -the fan is referred to by overall reference 1' ).
  • the features previously described with reference to at least one cross section according to a section plane perpendicular to the axis of rotation ARG of the fan 5 can be also referred to a plurality of cross sections located along at least a fourth, a third, half, two thirds, three fourths, or more preferably on the entire axial length of the impeller 5.
  • the fan 1 can be set up not only in a fan coil of an air conditioning, cooling, or heating hydronic system, but for example also in a split of a direct-expansion air conditioning, cooling, or heating system.
  • an exemplary embodiment means that a specific feature or structure described in connection with said embodiment is comprised in at least one embodiment of the invention and particularly in a particular variation of the invention as defined in a main claim.
  • the used materials, as well as the size can be any depending on the technical requirements.
  • references to a "first, second, third, ... n-th entity" have the only purpose of distinguishing them from each other, but indicating the n-th entity does not necessarily imply the existence of the first, second ... (n-1)th entity.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
EP23188586.4A 2022-08-02 2023-07-31 Ventilateur à flux transversal, ventilo-convecteur comprenant ledit ventilateur et procédé de réglage dudit ventilo-convecteur Pending EP4317698A1 (fr)

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IT102022000016374A IT202200016374A1 (it) 2022-08-02 2022-08-02 Ventilatore cross flow, fan coil provvisto di tale ventilatore e procedimento per installare tale fan coil.

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EP4317698A1 true EP4317698A1 (fr) 2024-02-07

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EP23188586.4A Pending EP4317698A1 (fr) 2022-08-02 2023-07-31 Ventilateur à flux transversal, ventilo-convecteur comprenant ledit ventilateur et procédé de réglage dudit ventilo-convecteur

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Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US507445A (en) 1893-10-24 Paul mortier
US2942773A (en) 1953-07-17 1960-06-28 Paul Pollrich & Comp Fans
US4958504A (en) * 1988-06-17 1990-09-25 Matsushita Electric Industrial Co., Ltd. Air conditioning apparatus for use in automobile
JPH04228318A (ja) * 1989-10-25 1992-08-18 Matsushita Electric Ind Co Ltd 車輌用空気調和装置
JP2000329367A (ja) * 1999-05-17 2000-11-30 Mitsubishi Heavy Ind Ltd クロスフローフアン
CN102889240B (zh) * 2011-07-22 2015-11-18 重庆圣锦汽车配件有限公司 风机内涡壳

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US507445A (en) 1893-10-24 Paul mortier
US2942773A (en) 1953-07-17 1960-06-28 Paul Pollrich & Comp Fans
US4958504A (en) * 1988-06-17 1990-09-25 Matsushita Electric Industrial Co., Ltd. Air conditioning apparatus for use in automobile
JPH04228318A (ja) * 1989-10-25 1992-08-18 Matsushita Electric Ind Co Ltd 車輌用空気調和装置
JP2000329367A (ja) * 1999-05-17 2000-11-30 Mitsubishi Heavy Ind Ltd クロスフローフアン
CN102889240B (zh) * 2011-07-22 2015-11-18 重庆圣锦汽车配件有限公司 风机内涡壳

Non-Patent Citations (2)

* Cited by examiner, † Cited by third party
Title
BRUNO ECK: "Fans-Design and Operation of centrifugal, axial-flow and cross-flow fans", 1973, PERGAMON PRESS
THONG Q. DANGPETER R. BUSHNELL: "Progress in Aerospace Sciences", vol. 45, 2009, ELSEVIER, article "Aerodynamics of cross-flow fans and their application to aircraft propulsion and flow control", pages: 1 - 29

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