EP2921712A1 - Rotor destiné à un ventilateur radial et ventilateur radial - Google Patents
Rotor destiné à un ventilateur radial et ventilateur radial Download PDFInfo
- Publication number
- EP2921712A1 EP2921712A1 EP15157598.2A EP15157598A EP2921712A1 EP 2921712 A1 EP2921712 A1 EP 2921712A1 EP 15157598 A EP15157598 A EP 15157598A EP 2921712 A1 EP2921712 A1 EP 2921712A1
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- EP
- European Patent Office
- Prior art keywords
- rotor
- housing
- ranges
- blades
- main
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
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- 230000008878 coupling Effects 0.000 description 2
- 238000010168 coupling process Methods 0.000 description 2
- 238000005859 coupling reaction Methods 0.000 description 2
- 238000013016 damping Methods 0.000 description 2
- 238000005265 energy consumption Methods 0.000 description 2
- 239000012530 fluid Substances 0.000 description 2
- 239000000203 mixture Substances 0.000 description 2
- 238000000465 moulding Methods 0.000 description 2
- 229910000838 Al alloy Inorganic materials 0.000 description 1
- 230000009102 absorption Effects 0.000 description 1
- 238000010521 absorption reaction Methods 0.000 description 1
- XAGFODPZIPBFFR-UHFFFAOYSA-N aluminium Chemical compound [Al] XAGFODPZIPBFFR-UHFFFAOYSA-N 0.000 description 1
- 229910052782 aluminium Inorganic materials 0.000 description 1
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- 238000007599 discharging Methods 0.000 description 1
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- 230000003068 static effect Effects 0.000 description 1
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Images
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/26—Rotors specially for elastic fluids
- F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
- F04D29/281—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for fans or blowers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/26—Rotors specially for elastic fluids
- F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
- F04D29/30—Vanes
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/40—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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
- F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps
- F04D29/666—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps by means of rotor construction or layout, e.g. unequal distribution of blades or vanes
Definitions
- the present invention relates to a rotor for a radial fan and a radial fan provided with such rotor.
- Radial fans in particular fans intended to send air and/or gas (frequently in the form of a mixture thereof) to boilers, such as condensation boilers, comprise a housing provided with a suction aperture and a discharge aperture for the air. Inside the housing a rotor is arranged capable of rotating about an axis of rotation. The air enters the housing through the suction aperture in the axial direction, crosses the rotor and is discharged from it in the radial direction into a spiral portion of the housing, from which the air reaches the discharge aperture. To convey the air along said path, the rotor is provided with a plurality of blades arranged around the rotation axis of the rotor having an arched profile in the direction transversal to the rotation axis.
- Radial fans must be able to provide adequate head in clearly defined flow intervals (so-called “working curves”) to ensure the correct functioning for example of the condensing boiler to which they are connected.
- a further strongly felt need is to limit the energy consumption related to the operation of the rotor, usually set in motion by an electric motor.
- a further need felt is to be able to provide a fan which can achieve a high increase in static pressure of the conveyed air with a relatively small air flow. This is for example a key feature for making efficient heat exchangers of a compact size.
- the purpose of the present invention is to make available a rotor for a radial fan and a radial fan which make it possible to achieve an efficient flow-head curve, in particular, appropriate to the operation of condensation boilers, such as not to requiring an excessive power consumption to drive the rotor, and to have overall limited dimensions.
- a radial fan is globally denoted by reference numeral 1.
- the fan 1 is, for example, suitable to convey air and/or gas (also in the form of a mixture thereof) towards a burner or a boiler or a general heating system.
- the fan 1 is particularly suitable to convey air and/or gas towards a condensation boiler.
- the fan 1 comprises a rotor 2 able to rotate about a rotation axis A, in particular inside a housing 3 of the fan.
- a rotor 2 able to rotate about a rotation axis A, in particular inside a housing 3 of the fan.
- the terms “axial” and “radial” refer to the rotation axis A of the rotor 2, unless otherwise specified.
- the housing 3 preferably comprises two separate connectable parts, such as a half-shell 4 which defines a rotor space 6 suitable to receive within it the rotor 2 and a cover 5 suitable to close the rotor space 6.
- the half-shell 4 and the cover 5 can be connected to each other for example by means of threaded connection members 7.
- the cover 5 may further comprise a projecting portion 5' suitable to be inserted with a shaped coupling in the rotor space 6 delimited by the half-shell 4, advantageously substantially complementary to it.
- the cover 5 is suitable to support a motor 8, preferably electric, intended to move the rotor 2 by means of its shaft 9 which, with the fan 1 assembled, is coaxial to the rotation axis A.
- the motor 8 may be connected to the cover 5 by means of an intermediate support 10 provided for connection to the cover 5, for example by means of screws 11 to be inserted in corresponding screw seats 12 of the cover 5.
- the screw seats 12 are arranged along a circumference at constant angular distances.
- the screw seats 12 may be three in number and spaced from each other by 120°.
- the intermediate support 10 may be provided with as many radial brackets 15 correspondingly distributed to the screw seats 12 of the cover 5.
- the fan 1 may comprise means for damping the vibrations.
- damping means of the vibrations comprise first dampers 13 suitable to act between the intermediate support 10 and the cover 5, for example rubber elements provided with a through opening for the passage of the screws 11, so as to dampen the vibrations parallel to the rotation axis A.
- the fan 1 may further comprise second dampers 14, acting between the intermediate support 10 and the cover 5 oriented and shaped so as to dampen the vibrations transmitted from the motor 8 to the housing 3 along radial directions.
- the second dampers 14, for example rubber elements, may be inserted in brackets 16 formed by or connected to the cover 5, and preferably arranged along an inner circumference to the circumference along which the screw seats 12 are arranged. Even more preferably such brackets 16 are three in number and arranged at 120° relative to one another.
- the second dampers 14 may for example be placed laterally in contact with the intermediate support 10, so as to act in the radial direction between the latter and the brackets 16.
- the latter may comprise a cover element 17 connected to the motor 8, for example by screws 18.
- Said cover element 17 is preferably cup-shaped, so as make the motor 8 inaccessible once the fan 1 has been assembled.
- the cover element 17 may have the function of protecting, in addition to the motor 8, one or more further auxiliary elements 48, such as electronic control circuits of the motor 8.
- the cover 5 comprises a through aperture 19.
- the fan 1 comprises a suction aperture 20 and a discharge aperture 21 for the air and/or gas.
- the suction aperture 20 and the discharge aperture 21 are made in the half-shell 4.
- the suction aperture 20 is preferably arranged laterally on the half-shell 4 and shaped so that the incoming air and/or gas enters the rotor space 6 and reaches the rotor 2 along a substantially axial direction.
- the discharge aperture 21 is preferably made at one end 23 of a discharge portion 22 of the half-shell 4 which extends in a direction substantially tangential to the housing 3 ( figures 9 , 15 , 17 ), so that the air and/or gas discharged by the rotor 2 circulates in the rotor space 6 along substantially tangential flow lines and is discharged by the fan 1 through the discharge aperture 21 without undergoing excessive deviations in its motion.
- a flange 24 may be provided suitable to connect the fan 1 to outer support elements (not shown in the figures), for example by means of threaded connection elements.
- the rotor 2 comprises a plurality of main blades 25 arranged in succession around the rotation axis A ( figures 2 , 5 , 20 , 21 ).
- Each of the main blades 25 has a radially more inward leading end 32 and a radially more outward trailing end 33.
- the leading end 32 has the function of aspirating and capturing the air and/or gas coming in the axial direction from the suction aperture 20 and the trailing end 33 has the function of guiding the air and/or gas discharged by the rotor 2 into the rotor space 6 of the housing 3.
- Each of the main blades 25 comprises a concave primary surface of the main blade 26 and a convex secondary surface of the main blade 27 opposite the primary surface of the main blade 26. This way, each of the main blades 25 has a substantially arched shape. Furthermore, the secondary surface of the main blade 27 of each of the main blades 25 faces toward the primary surface of the main blade 26 of the next main blade. This way, between two successive main blades of a pair of main blades a flow passage 28 is formed for conveying the air and/or gas between a radially inner position and a radially outer position of the rotor 2.
- the rotor 2 rotating as a result of operation by the motor 8, aspirates the air and/or gas from the suction aperture 20 of the housing 3, coaxial to the rotor 2, and conveys it by effect of the rotation of the rotor into the flow passages 28 delimited by the main blades 25, lastly discharging it radially outside the rotor 2 in the rotor space 6.
- the main blades 25 are shaped so as to optimise the fluid dynamics inside the rotor and thus the overall performance of the fan 1.
- the main blades 25 are free from twisting (i.e. the chord angle of the split is constant and the chord is parallel to the rotation axis A) and, in a cross-section plane perpendicular to the rotation axis A, extend along an arc of a circle with a substantially constant radius of curvature R1, preferably in the range from 140mm to 180mm, preferably from 150mm to 170mm, even more preferably about 159mm.
- the rotor 2 further comprises a plurality of auxiliary blades 29 (so-called “splits”) also arranged around the rotation axis of the rotor 2, and having a radial extension and length less than the radial extension and length of the main blades 25.
- the main blades 25 and the splits 29 alternate, so that in each of the flow passages 28 only one of the splits 29 is provided for.
- each of the splits 29 has a radially inner leading end 34 and a radially outer trailing end 35. Furthermore, each of the splits 29 comprises a concave split primary surface 30 and a convex split secondary surface 31 opposite the split primary surface 30 of said split 29 ( figures 2 , 5, 6 ).
- the split primary surface 30 of each of the splits 29 faces towards the secondary surface of the main blade 27 of a first of the main blades 25 between which the split 29 is positioned and the secondary split surface 31 of each of the auxiliary blades 29 faces toward the primary surface of the main blade 26 of a second of the main blades 25 between which is the split 29 is positioned.
- the splits 29 are free from twisting (i.e. the chord angle of the split is constant and the chord is parallel to the rotation axis A) and, in a cross-section plane perpendicular to the rotation axis A, extend along an arc of a circle with a substantially constant radius of curvature R2, preferably in the range from 140mm to 180mm, preferably from 150mm to 170mm, even more preferably about 159mm.
- the radius of curvature R2 of the splits 29 is substantially equal to the radius of curvature R1 of the main blades 25.
- the main blades 25 and splits 29 thus preferably have the shape of cylindrical wall portions extending in a direction parallel to the rotation axis A and with a constant radius of curvature R1, R2 in the section planes orthogonal to the rotation axis A.
- the blades in addition to the shape described, have an adequate spatial arrangement inside the rotor as well as a suitable orientation at their leading and trailing ends where the air and/or gas are respectively suctioned and discharged.
- the trailing end 33 it is possible to draw a straight line T outpp tangent to the arc of the main blade and a further radial straight line R outpp which connects said trailing end 33 with the centre of the rotor, i.e. with the rotation axis A.
- Said two straight lines T outpp and R outpp identify a main blade output angle ⁇ outpp which, advantageously, is between -5° and +5° and which preferably is approximately 0°. Therefore, according to a preferred embodiment, the trailing end of the main blade 33 is oriented exactly in a radial direction to the rotation axis A.
- the split output angle ⁇ outps may be between -5° and + 5° and is preferably equal to about 0°.
- the split input angle ⁇ inps may be between 4° and 6° and is preferably equal to about 4.7°.
- the split wrap angle ⁇ ps may be between 7° and -3° and is preferably equal to about 2°.
- the trailing ends 33 of the main blades 25 are arranged so as to define an outer rotor circumference which substantially delimits the maximum radial dimensions of the rotor.
- the leading ends 32 of the main blades 25 are arranged so as to define an inner circumference of the main blades.
- the outer circumference of the rotor and the inner circumference of the main blades respectively have a rotor diameter D max and an inner diameter of the main blades d ipp ( Figure 4 ) which, advantageously, have a dimensionless ratio D max / D ipp in the range between 5 and 7 and which is preferably approximately equal to 5.9 .
- the rotor 2 has an axial rotor height h ext ( figure 4 ).
- the rotor diameter D max and the axial rotor height h ext have a ratio D max / H ext in the range from 4 to 5, and preferably equal to about 4.91.
- the trailing ends 35 of the splits 29 are also arranged along the outer rotor circumference ( figures 4 , 5 ). Furthermore, their leading ends 34 are arranged so as to define a split inner circumference with a split blade inner diameter d ips .
- the rotor diameter D max and the split inner diameter D ips have a ratio D max / D ips in the range from 1.55 to 1.65, preferably equal to about 1.59.
- the geometric parameters may be chosen as follows:
- the rotor 2 comprises a hub element 36 intended to be connected to the shaft 9 of the motor 8 to drive the rotor 2.
- the hub element 36 forms a guide surface 51 facing a front side 50 of the rotor 2 intended to face towards the suction aperture 20 of the housing 3.
- the main blades 25 and the splits 29 protrude from the guide surface 51 and, during the rotational movement of the rotor 2 inside the housing 3, the air and/or the gas is guided from the suction aperture 20 along the guide surface 51 in the flow passages 28 defined between the main blades 25.
- the air or gas is forced to change direction from a direction initially mainly axial (with respect to the rotation axis A) to a mainly radial and circumferential direction relative to the rotation axis A.
- the guide surface 51 is a rotation surface around the rotation axis A, preferably annular, or alternatively circular, with double curvature generatrix which forms a convex radially inner portion 52 to which an intermediate concave portion 53 connects (in a step or interruption free point of inversion).
- the intermediate portion 53 connects to a substantially rectilinear radially outer portion 54 which forms an outer ring that is planar and orthogonal to the rotational axis A.
- the guide surface 51 has the shape of an axially compressed or flattened bell, similar to a Gaussian bell, with the effect of reducing the transversal mixing, and turbulence effects between the molecules of the gas conveyed.
- the radially inner 52 and intermediate 53 portions of the generatrix of the guide surface 51 are in the shape of an arc of a circle in which the curvature radius R52 of the radially inner portion 52 is less than the curvature radius R53 of the intermediate portion 53, preferably R52 ⁇ 0.7*R53, even more preferably R52 is about 0.5*R53.
- the ratio D54ex/Dmax between an outer diameter D54ex of the guide surface 51 and an outer diameter Dmax of the rotor 2 is advantageously in the range from 0.7 to 0.85, preferably about 0.76.
- the ratio D53ex/D54ex between an outer diameter D53ex of the concave intermediate portion 53 of the generatrix of the guide surface 51 and an outer diameter D54ex of the guide surface 51 is advantageously in the range from 0.75 to 0.89, preferably about 0.83.
- the aforementioned geometrical parameters may be chosen as follows:
- the rotor 2 may also comprise a peripheral support ring 37, placed in a position axially opposite the hub element 36 and which forms an aperture 38 overlapping in the axial direction (relative to the rotation axis A) with the hub element 36.
- the support ring 37 With the fan assembled, the support ring 37 is positioned around the suction aperture 20 of the housing 3. This way, during the rotational movement of the rotor 2, the air and/or the gas is guided from the suction aperture 20 through the aperture 38 along the guide surface 51 and along an inner surface 56 of the support ring 37 which partially close on two axially opposite sides the flow passages 28 delimited by the blades 25, 29, thereby imposing on the air and/or gas to transit inside them.
- the support ring 37 is connected to all the main blades 25 and splits 29 on a front side thereof axially opposite the guide surface 51 of the hub element 36.
- the hub element 36, support ring 37 and the main and secondary blades are made in one piece, e.g. using a moulding process, preferably in plastic material.
- the hub element 36 and the support ring 37 are arranged so that the projection of the hub element 36 on the support ring 37 along the rotation axis of the rotor A is at or inside the aperture 38 of the support ring 37.
- the aperture 38 is circular in shape and the hub element 36 has also a circular shape with dimensions equal or inferior (preferably slightly smaller) to those of the aperture 38.
- the hub element 36 and the support ring 37 are mutually connected both by means of the main blades 25 and the splits 29 ( figure 4 ), which have their leading ends 32, 34 on the hub element 36 and comprise connection portions 40 in which their height (in the axial direction A of the rotor) increases gradually from such leading ends 32, 34 radially outwardly until reaching the maximum value in a radially inner area with respect to the support ring 37.
- the main blades 25 and splits 29 extend radially (but not in a perfectly radial direction, but with the curvature described above) outwardly along the support ring 37 up to their trailing ends 33, 35 ( figures 3 , 5 , 19, 20 ).
- the trailing ends 33 of the main blades 25 and the splits 29, which define the rotor circumference of diameter D max end exactly flush with an outer circumference of the support ring 37 ( figure 4 ).
- the outer diameter D37ex of the support ring 37 corresponds exactly with the outer diameter Dmax of the rotor 2 and the ratio Dmax/D37int between the outer diameter Dmax of the rotor 2 and an inner diameter D37int of the support ring 37 is in the range 1.1 to 1.3, preferably about 1.22.
- D37int may be chosen in the range of 73mm ... 73.9mm ... 75mm.
- a front edge of the main blades 25 forms the aforementioned substantially straight connection portion 40 seen in a circumferential direction relative to the axis of rotation A, to which an outer continuously convex portion connects, for example formed of an intermediate arc of circle portion 57 having a radius of curvature R57 and a radially outer portion 58 of an arc of circle having a radius of curvature R58 (at the support ring 37), wherein the ratio R57/R58 of the two curvatures may advantageously be in the range from 0.18 to 0.22, preferably about 0.2.
- the aforementioned geometrical parameters may be chosen as follows:
- the ratio D25alt/Dmax between a diameter D25alt of the point of maximum axial height of the main blade 25 and the outer diameter Dmax of the rotor 2 may advantageously be in the range from 0.45 to 0.6, preferably about 0.52.
- the hub element 36 advantageously comprises a tubular portion 42 suitable to receive the shaft 9 of the motor 8 and which preferably extends parallel to the rotation axis A of the rotor 2.
- the shaft 9 may be connected to the tubular portion 42 by means of locking means (not shown in the figures) suitable to connect the latter integrally in rotation and in translation along the rotation axis A.
- the hub element 36 may form a discontinuity with respect to the curvature of the guide surface 51 described ( figures 4 , 20 ).
- the number of main blades 25 is seventeen and the number of splits 29 is seventeen.
- the main blades 25 and the splits 29 may have a substantially constant thickness s pp and s ps equal to about 1.15mm (at the slimmer end) ... 1.8mm.
- the axial height of the housing H all may be 19.2mm ... 19.8mm ... 20.3mm.
- the rotor space 6 of the housing 3, transversally to its height H all , and thus transversely to the rotation axis A of the impeller 2, is delimited by a transversal profile which comprises a main section 45 advantageously shaped as a plurality of successive housing circular arcs ( figures 9 , 15 , 17 ).
- the transversal profile of the rotor space 6 may further comprise a discharge portion 46, in which the housing 3 extends into the discharge portion 22, identified by a reference angle ⁇ .
- the main section 45 comprises four of the aforesaid successive housing circular arcs, in particular a first CC1, a second CC2, a third CC3, and a fourth CC4 arc of a circle of housing respectively having a first housing radius of curvature RC1, a second housing radius of curvature RC2, a third housing radius of curvature RC3, and a fourth housing radius of curvature RC4.
- These arcs of circles of housing are disposed in an order, preferably starting more or less from the discharge portion 46, with a direction opposite to that of rotation of the rotor 2.
- the arcs of circles of housing are arranged counter-clockwise, while the rotor is intended to rotate clockwise.
- the aforementioned geometrical parameters may be chosen as follows:
- radii of curvature of housing RC1, RC2, RC3, RC4 are decreasing from RC1 to RC4, namely counter-clockwise in figure 9 .
- the housing arcs of circle are advantageously connected so that the main section 45 of the transversal profile of the rotor space 6 is substantially free of discontinuities.
- the discharge portion 46 may have a width ⁇ between 60° and 80°, preferably equal to about 70°.
- the housing 3 comprises a guide tongue 47 suitable to convey the air and/or gas discharged radially by the rotor 2 towards the discharge portion 22 and from there towards the discharge aperture 21 ( figures 9 , 11- 13 , 15 , 17 ).
- This guide tongue 47 preferably cantilevered formed in a single piece with the half-shell 4 of the housing 3, is placed in the rotor space 6 at the discharge portion 46.
- the guide tongue 47 forms a curved radially inner surface 59 (facing the rotor space 6) substantially with said fourth radius of curvature of housing RC4, and a radially outer surface 60 with a double curvature with a convex portion remote from the discharge aperture 21 and a concave portion next to the discharge aperture 21.
- the guide tongue 47 has a cross-section that increases gradually in the direction of the rotation axis A towards the discharge aperture 21 ( figure 13 ), so as to force the air and/or gas discharged by the rotor to follow a circumferential path along the entire rotor space before reaching the discharge portion 22. Moreover, the guide tongue 47 has a cross-section which gradually increases in a direction radial to the rotation axis A towards the discharge aperture 21 ( figure 13 ).
- the housing 3, in particular the half-shell 4 and the cover 5, are preferably made of aluminium or aluminium alloy.
- the fan 1 thus configured is able to guarantee high head values and that do not undergo excessive variations as the flow rates dispensed vary. It has also been verified that the power absorbed by the electric motor for operating the fan at the working pressures and flow rates is maintained at sufficiently low levels.
- the overall dimensions of the fan due essentially to the axial and radial dimensions of the rotor, which determine the axial and radial dimensions of the housing, are suitable for applications for which the fans according to the invention are intended, in particular for the supply of air and/or gas to condensing boilers.
- FIGS 21 , 22, 23 illustrate an embodiment of a rotor and a fan which have several features in common with the fan described so far, but which differ in some details that will emerge from the following brief description:
- the main blades 25 are free of twisting, and in a cross-section plane perpendicular to the rotation axis A, extend along an arc of a circle with a substantially constant radius of curvature R1, preferably in the range from 575mm to 625mm, preferably approximately 599mm.
- the splits 29 are free of twisting, and in a cross-section plane perpendicular to the rotation axis A, extend along an arc of a circle with a substantially constant radius of curvature R2, preferably in the range from 575mm to 625mm, preferably approximately 599mm.
- the radius of curvature R2 of the splits 29 is substantially equal to the radius of curvature R1 of the main blades 25.
- the ratio D max / D ipp between the outer rotor circumference Dmax and the inner circumference of the main blades d ipp is in the range from 3.5 to 5.5, preferably about 4.6 .
- the rotor diameter D max and the axial rotor height h ext have a ratio D max / H ext in the range from 7 to 7.5, and which is preferably equal to about 7.27.
- the rotor diameter D max and the split inner diameter D ips have a ratio D max / D ips in the range from 1 to 2, preferably equal to about 1.5.
- geometric parameters may be chosen as follows:
- the hub element 36 forms a guide surface 51 from which the main blades 25 and the splits 29 protrude and which is a rotation surface with respect to the rotation axis A, preferably annular or alternatively circular, with double curvature generatrix which forms a convex radially inner portion 52 to which an intermediate concave portion 53 connects (in a stepless or interruption-free point of inversion).
- the intermediate portion 53 connects to a substantially rectilinear radially outer portion 54 which forms an outer ring that is planar and orthogonal to the rotational axis A.
- the guide surface 51 has the shape of an axially compressed or flattened bell, similar to a Gaussian bell, with the effect of reducing the transversal mixing, and turbulence effects between the molecules of the gas conveyed.
- the radially inner 52 and intermediate 53 portions of the generatrix of the guide surface 51 are composed of series of arcs of a circle in which the curvature radius R52 of the radially inner portion 52 is less than the curvature radius R53 of the intermediate portion 53.
- the ratio D54ex/Dmax between an outer diameter D54ex of the guide surface 51 and an outer diameter Dmax of the rotor 2 is advantageously in the range from 0.7 to 0.75, preferably about 0.72.
- the ratio D53ex/D54ex between an outer diameter D53ex of the concave intermediate portion 53 of the generatrix of the guide surface 51 and an outer diameter D54ex of the guide surface 51 is advantageously in the range from 0.85 to 0.95, preferably about 0.9.
- the outer diameter D37ex of the support ring 37 is inferior to the outer diameter Dmax of the rotor 2.
- the ratio Dmax/D37int between the outer diameter Dmax of the rotor 2 and an inner diameter D37int of the support ring 37 is in the range from 1.2 to 1.3, preferably about 1.25.
- the ratio Dmax/D37ext between the outer diameter Dmax of the rotor 2 and the outer diameter D37ext of the support ring 37 is in the range from 1.02 to 1.1, preferably about 1.04.
- D37int may be chosen in the range of 92mm ... 96mm ... 100mm and D37ext may be chosen in the range 113mm.. 115.3 mm ... 117mm.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
ITMI20140429 | 2014-03-17 |
Publications (2)
Publication Number | Publication Date |
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EP2921712A1 true EP2921712A1 (fr) | 2015-09-23 |
EP2921712B1 EP2921712B1 (fr) | 2019-11-20 |
Family
ID=50733174
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP15157598.2A Active EP2921712B1 (fr) | 2014-03-17 | 2015-03-04 | Rotor destiné à un ventilateur radial et ventilateur radial |
Country Status (2)
Country | Link |
---|---|
EP (1) | EP2921712B1 (fr) |
ES (1) | ES2773899T3 (fr) |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2019025710A1 (fr) * | 2017-08-02 | 2019-02-07 | Valeo Systemes Thermiques | Roue de type centrifuge pour groupe moto-ventilateur |
FR3069896A1 (fr) * | 2017-08-02 | 2019-02-08 | Valeo Systemes Thermiques | Roue de type centrifuge pour groupe moto-ventilateur |
CN110242598A (zh) * | 2018-03-08 | 2019-09-17 | 日本电产株式会社 | 离心风扇 |
WO2020015902A1 (fr) | 2018-07-19 | 2020-01-23 | Arcelik Anonim Sirketi | Appareil de soufflage d'air supplémentaire pour ventilateurs radiaux et ventilateur radial |
Citations (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB2317926A (en) * | 1996-10-03 | 1998-04-08 | Elta Fans Ltd | Fan with flow deflector |
US20020110455A1 (en) * | 2001-02-12 | 2002-08-15 | Kim Sung Chun | Turbo fan of a ceiling-embeded cassette type air conditioner having an improved structure |
US20040202539A1 (en) * | 2001-05-09 | 2004-10-14 | Andreas Blank | Rotor disk |
WO2006013067A2 (fr) | 2004-07-31 | 2006-02-09 | Ebm-Papst Landshut Gmbh | Roue de soufflante radiale |
WO2006106744A1 (fr) * | 2005-03-31 | 2006-10-12 | Mitsubishi Heavy Industries, Ltd. | Ventilateur centrifuge |
EP1744060A2 (fr) | 2005-07-12 | 2007-01-17 | Robert Bosch Corporation | Unité ventilateur centrifuge |
US20120315135A1 (en) * | 2010-07-16 | 2012-12-13 | Mitsubishi Heavy Industries, Ltd. | Multi-blade centrifugal fan and air conditioner using the same |
US20140023510A1 (en) * | 2012-07-17 | 2014-01-23 | Ruck Ventilatoren Gmbh | Diagonal impeller for a diagonal fan, and diagonal fan |
-
2015
- 2015-03-04 EP EP15157598.2A patent/EP2921712B1/fr active Active
- 2015-03-04 ES ES15157598T patent/ES2773899T3/es active Active
Patent Citations (8)
Publication number | Priority date | Publication date | Assignee | Title |
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GB2317926A (en) * | 1996-10-03 | 1998-04-08 | Elta Fans Ltd | Fan with flow deflector |
US20020110455A1 (en) * | 2001-02-12 | 2002-08-15 | Kim Sung Chun | Turbo fan of a ceiling-embeded cassette type air conditioner having an improved structure |
US20040202539A1 (en) * | 2001-05-09 | 2004-10-14 | Andreas Blank | Rotor disk |
WO2006013067A2 (fr) | 2004-07-31 | 2006-02-09 | Ebm-Papst Landshut Gmbh | Roue de soufflante radiale |
WO2006106744A1 (fr) * | 2005-03-31 | 2006-10-12 | Mitsubishi Heavy Industries, Ltd. | Ventilateur centrifuge |
EP1744060A2 (fr) | 2005-07-12 | 2007-01-17 | Robert Bosch Corporation | Unité ventilateur centrifuge |
US20120315135A1 (en) * | 2010-07-16 | 2012-12-13 | Mitsubishi Heavy Industries, Ltd. | Multi-blade centrifugal fan and air conditioner using the same |
US20140023510A1 (en) * | 2012-07-17 | 2014-01-23 | Ruck Ventilatoren Gmbh | Diagonal impeller for a diagonal fan, and diagonal fan |
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2019025710A1 (fr) * | 2017-08-02 | 2019-02-07 | Valeo Systemes Thermiques | Roue de type centrifuge pour groupe moto-ventilateur |
FR3069895A1 (fr) * | 2017-08-02 | 2019-02-08 | Valeo Systemes Thermiques | Roue de type centrifuge pour groupe moto-ventilateur |
FR3069896A1 (fr) * | 2017-08-02 | 2019-02-08 | Valeo Systemes Thermiques | Roue de type centrifuge pour groupe moto-ventilateur |
CN110242598A (zh) * | 2018-03-08 | 2019-09-17 | 日本电产株式会社 | 离心风扇 |
WO2020015902A1 (fr) | 2018-07-19 | 2020-01-23 | Arcelik Anonim Sirketi | Appareil de soufflage d'air supplémentaire pour ventilateurs radiaux et ventilateur radial |
Also Published As
Publication number | Publication date |
---|---|
ES2773899T3 (es) | 2020-07-15 |
EP2921712B1 (fr) | 2019-11-20 |
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