EP3181912A1 - Ventilateur centrifuge - Google Patents

Ventilateur centrifuge Download PDF

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Publication number
EP3181912A1
EP3181912A1 EP16199249.0A EP16199249A EP3181912A1 EP 3181912 A1 EP3181912 A1 EP 3181912A1 EP 16199249 A EP16199249 A EP 16199249A EP 3181912 A1 EP3181912 A1 EP 3181912A1
Authority
EP
European Patent Office
Prior art keywords
hub
air conveyor
base
blades
centrifugal fan
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.)
Granted
Application number
EP16199249.0A
Other languages
German (de)
English (en)
Other versions
EP3181912B1 (fr
Inventor
Mauro PERFETTIBILE
Daniele D'OVIDIO
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
AEROMECCANICA STRANICH SpA
Original Assignee
Peerfettibile Fanservice Srl
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Peerfettibile Fanservice Srl filed Critical Peerfettibile Fanservice Srl
Publication of EP3181912A1 publication Critical patent/EP3181912A1/fr
Application granted granted Critical
Publication of EP3181912B1 publication Critical patent/EP3181912B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
    • F04D29/281—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for fans or blowers
    • 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
    • F04D29/60—Mounting; Assembling; Disassembling
    • F04D29/62—Mounting; Assembling; Disassembling of radial or helico-centrifugal pumps
    • F04D29/624—Mounting; Assembling; Disassembling of radial or helico-centrifugal pumps especially adapted for elastic fluid pumps
    • F04D29/626—Mounting or removal of fans
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2230/00—Manufacture
    • F05D2230/20—Manufacture essentially without removing material
    • F05D2230/23—Manufacture essentially without removing material by permanently joining parts together
    • F05D2230/232—Manufacture essentially without removing material by permanently joining parts together by welding

Definitions

  • the present invention relates to a centrifugal fan having high performance according to the preamble of the main claim.
  • a centrifugal fan is an operating machine transmitting energy to the fluid crossing the same, thus causing a pressure increase.
  • the pressure increase in a fan is generally quite low, differently from the one that can be obtained by means of a compressor.
  • Centrifugal fans are used in a number of industrial processes, such as for example in industries for cement and steel production, in the dairy industry, in the industry for beverage production, such as for example beer.
  • Fans are classified, depending on the pressure increase they cause, in low pressure fans with static pressure at the outlet lower than 720 Pa, intermediate pressure fans with static pressure at the outlet comprised between 720 and 3600 Pa, and high pressure fans with static pressure at the outlet comprised between 3600 and 20000 Pa.
  • an industrial fan has rotational speed of some thousands of revolutions per minute, whereas a compressor reaches rotational speeds of some tens of thousands of revolutions per minute.
  • Centrifugal fans allow obtaining manometric compression ratios higher than axial fans.
  • centrifugal fans Due to different applications, industrial centrifugal fans have construction less strong than centrifugal compressors, are more lightweight and less expensive, as both manufacturing and operation costs.
  • centrifugal fans comprise a fan wheel and an outer casing termed volute having the aim of directing the air flow.
  • the fan wheel of a centrifugal fan is obtained from reciprocally welded sheet metals comprising a plurality of blades arranged around an axis, a disc-shaped base placed in the plane normal to the axis, to which the blades are welded, a hub coaxial to the axis, a closing element arranged on the edge of the blades.
  • the disc, the outer part of the hub and the closing element define a duct with an inlet and an outlet, inside which the blades are arranged and form many blade channels.
  • the operating fluid moves closer to the fan wheel in a substantially axial direction, crosses the inlet, encounters the base, which prevents a further motion in the axial direction, and is thus forced to abruptly change the direction of motion from axial to radial passing through the blade channels defined by the blades driving the fluid motion.
  • a higher number of blades allow having a better driven fluid, but at the same time increases pressure drops due to sliding friction. Since the duct widens radially, the blades at the inlet are more concentrated (lower blade pitch).
  • the implementation of the fan with reciprocally welded sheet metals allows having lightweight fans at low manufacturing cost.
  • centrifugal compressors are usually made by casted pieces subsequently cold worked, so as to obtain the desired geometry. Compressors are designed to support higher pressures and larger centrifugal stresses.
  • Compressors have therefore a more fluid-dynamically accurate geometry, but are heavier and have higher manufacturing cost.
  • the process for implementing the fan wheels of sheet metal comprises the steps of welding the blades to a base and eventually welding the hub to the fan wheel. Thereby the fan wheel, adequately stiffened by the blades, can be welded to the hub without significantly deforming.
  • centrifugal fans A problem with the currently manufactured centrifugal fans is the high electric power consumption, since they work for many hours per year.
  • Another problem is that the currently manufactured fans are noisy.
  • Object of the present invention is therefore to implement a centrifugal fan that allows overcoming the mentioned drawbacks, in particular an object is to implement a fan that, by keeping implementation costs low, allows having high efficiency and low energy consumption.
  • Another object is to improve the blade pitch at the inlet.
  • a further object is to reduce the noisiness of the fans.
  • the centrifugal fan is seen in the first embodiment as comprising a fan wheel apt to process an operating fluid between an inlet 10 and an outlet 11.
  • the operating fluid is in general air subjected to pressure increase between the inlet 10 and the outlet 11.
  • the fan wheel comprises an array of blades 1 arranged around an axis A between the inlet 10 and the outlet 11, a disc-shaped base 2, placed in the plane normal to the axis A, to which said blades 1 are welded, a hub 3 coaxial to the axis A, a closing element 5 arranged at the edge of the blades 1, an air conveyor 4 having axially symmetrical shape, rigidly connected to the base 2 and apt to gradually convey the fluid from a substantially axial motion at the inlet 10 to a substantially radial motion at the outlet 11.
  • the blades are inside the duct formed by the closing element 5, the base 2 and the air conveyor 4.
  • the hub 3 is a hollow cylindrical element apt to be arranged on a shaft and to transmit the drive shaft motion to the fan wheel, for example through a spline.
  • the air conveyor 4 is made in a piece separate from the hub 3 and is directly and rigidly connected to the base 2, the latter being directly and rigidly connected to the hub 3.
  • the blades 1, the base 2, the air conveyor 4 and the closing element 5 are made of sheet metal and the mutual rigid connections are made by welding.
  • the air conveyor 4 made of sheet metal, is welded to the base 2, the blades 1 and the hub 3.
  • the blades 1 are welded to the base 2, the air conveyor 4 and the closing element 5.
  • the air conveyor 4 is obtained from a planar sheet metal bent to form a frusto-conical surface and arranged such that the unit vector normal to the surface forms an angle of about 45° to the axis A.
  • the air conveyor 4 has a curved longitudinal section, as in fig. 1 , and is obtained by bending a sheet metal for example through deep-drawing or calendering or cold molding processes.
  • a first cavity 8 is formed between the air conveyor 4, the base 2 and the hub 3.
  • the air conveyor 104 is spaced apart from the hub 103 at the inlet 110 in order to have an inlet area no longer dependent on the hub section.
  • the fan wheel of the centrifugal fan comprises a connecting structural element 106 between the hub 103 and the air conveyor 104, which is apt to counter the centrifugal stresses.
  • connecting structural element 106 is important especially in case the fan wheel is large-sized.
  • the plug 107 connected to the air conveyor 104 closes a cavity 112 delimited by the portion of base 102 closest to the hub 103.
  • Said connecting structural element 106 arranged inside the cavity 112, is not contacting with the operating fluid processed by the fan, but is however contacting with the air being generally inside the cavity 112.
  • the connecting structural element 106 has shape with low aerodynamic resistance when the fan wheel rotates and can have for example the shape of a disc or one or more spokes which are elongated parallel to the plane of rotation perpendicular to the axis A and thin in the longitudinal one, so as to oppose low resistance to the rotation.
  • the hub is seen as having a terminal machined in such a way to form a spacer 114.
  • Such a spacer 114 is comprised within the connecting structural elements. It results from the continuation of the hub 103 towards the air conveyor 104 and is formed from one piece with the conveniently turned hub 103.
  • the inlet 110 has the shape of an annulus wherein the inner circumference is separated from the hub 103. In this way, the blades at the inlet are more spaced from the axis A, in order to increase the free passage and can be extended in the axial direction to obtain an inductor.
  • the plug 107 closes a third cavity 112, defined by the air conveyor 104 and the hub 103, and contains the connecting structural elements.
  • first, second and third cavities 8, 9 and 112 are apt to allow vacuum to be obtained in their inside, so that to reduce even more the losses by friction with the air in their inside, that would otherwise form vortexes originating dissipations.
  • the blades advantageously go up along the axial direction at the inlet and the edge of the blades at the inlet is slightly bent, as shown in fig. 1 , in order to facilitate the fluid input and to obtain what is termed an inductor.
  • the blades, the base, the air conveyor, the closing element and the connecting structural elements are made of sheet metal and welded one to another.
  • the process for implementing the different embodiments of sheet metals differs from the one followed for implementing known fans.
  • the hub is in fact welded to the base before the blades and the air conveyor are welded to the base, since it would be difficult, if not impossible, implementing the welding between hub and air conveyor after the air conveyor has been welded to the base and blades.
  • the assembling sequence is the following:
  • steps d) and e) precede step c) and the hub is welded to the base after the connecting structural elements have been welded to the hub.
  • the welding of the hub to the base 2 occurs before the welding of all the blades to the base 2.
  • the inner surface of the hub is turned to be perfectly circular, and the fan wheel is balanced with some weights in order to limit unbalances due to centrifugal forces.
  • some parts as the blades or the air conveyor 4 are made of plastic material, such as for example a glass fiber or carbon fiber composite material.
  • the curve of the static pressure at the outlet for the fan according to the invention is by far less dependent on the required flow rate, with respect to the same curve for a conventional fan.
  • the fan according to the invention allows obtaining it at lower speed of rotation of the rotor, and therefore with remarkable energy saving.
  • the fan wheel implemented according to the invention has efficiency of about 4% higher than the efficiency of the fan wheel implemented according to known art, whereas for a flow rate of 5000 m 3 /h the efficiency increases by about 16%, as further evidence of lower energetic consumption.
  • a flow for example of air or vapor enters the inlet 10 of the centrifugal fan according to the invention and moves in a substantially axial direction, inserts in the blade channels by running across the inductor and being accelerated and compressed.
  • the air conveyor In its motion it encounters the air conveyor that diverts the flow in a substantially radial direction and gradually leads it with its concave surface.
  • the flow In the motion diversion, the flow is driven by the blades and the air conveyor, such that the change of direction occurs gradually and by limiting the turbulence generated by abrupt changes of direction and subjecting the fluid to compression as similar as possible to reversible adiabatic or isentropic one.
  • the fan provides mechanic power to the fluid that then exits from the outlet.
  • the air conveyor 4, 104 is supported by the connecting structural elements having a small longitudinal section and thus offering low resistance to the rotation caused by the air friction.
  • the inlet is spaced from the axis A and the outer surface of the hub.
  • the radiused air conveyor comprises a sheet metal forming a truncated cone.
  • the air conveyor is made of bent sheet metal, for example deep-drawn, and has a curved longitudinal section, as in figures 2, 3 and 4 .
  • the closing element is welded to the edge of the blades and rotates with them.
  • the blades do not extend beyond the closing element, whereby they are inside the duct formed by the closing element on the outside and the base, the radiused air conveyor and possibly the hub on the inside.
  • the fan according to the invention achieves two effects: it reduces the turbulence of the processed fluid and reduces the friction with the air of the surrounding environment.
  • the fan wheel is symmetrical with respect to the plane normal to the axis A passing though the base.
  • the fan can process twice the flow rate while being compact.
  • the air conveyor since it is radiused, reduces the motion turbulence of the fluid processed by the fan, pressure drops are reduced and the pressure at the outlet can be higher, the rotation speed of the fan wheel being the same.
  • the aerodynamically-shaped connecting structural elements contribute to reduce pressure drops by friction with the surrounding air.
  • the plug and vacuum in the cavities further reduce losses by air friction and this allows reducing the electric power the fan requires.
  • the smaller turbulences due to the air conveyor allow obtaining, the other parameters remaining the same, higher manometric compression ratios (equal to the ratio between the static pressure at the outlet and the static pressure at the inlet), whereby the fan can be used also in fields in which low end compressors are currently used.
  • the smaller turbulences also allow having lower wear of the fan wheel in case the processed fluid contains solid and thus abrasive particles.
  • An advantageous feature of the invention is that the connecting structural elements arranged at the inlet allow the duct through which the fluid flows to be spaced from the axis and widening the inlet area in order to have better distribution of the blades, with lower losses at the inlet.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
EP16199249.0A 2015-12-15 2016-11-17 Ventilateur centrifuge Active EP3181912B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
ITUB2015A009662A ITUB20159662A1 (it) 2015-12-15 2015-12-15 Ventilatore centrifugo a elevate prestazioni.

Publications (2)

Publication Number Publication Date
EP3181912A1 true EP3181912A1 (fr) 2017-06-21
EP3181912B1 EP3181912B1 (fr) 2019-09-04

Family

ID=55642765

Family Applications (1)

Application Number Title Priority Date Filing Date
EP16199249.0A Active EP3181912B1 (fr) 2015-12-15 2016-11-17 Ventilateur centrifuge

Country Status (2)

Country Link
EP (1) EP3181912B1 (fr)
IT (1) ITUB20159662A1 (fr)

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH301112A (de) * 1950-10-27 1954-08-31 Maschf Augsburg Nuernberg Ag Laufrad für Zentrifugallüfter mit axialem Eintritt und radialem Austritt.
US3221398A (en) * 1961-01-25 1965-12-07 Ruth D Mayne Method of manufacturing a turbine type blower wheel
US4363601A (en) * 1979-01-19 1982-12-14 Oy Nokia Ab Impeller in a centrifugal blower
US5336050A (en) * 1993-05-06 1994-08-09 Penn Ventilator Co. Inc. Ventilator fan device
DE10310981A1 (de) * 2003-03-07 2004-09-23 Piller Industrieventilatoren Gmbh Laufrad für Gebläse
WO2005073559A1 (fr) 2004-01-23 2005-08-11 Robert Bosch Gmbh Ventilateur centrifuge
EP1138954B1 (fr) 2000-03-30 2009-12-16 Technofan Ventilateur centrifuge

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH301112A (de) * 1950-10-27 1954-08-31 Maschf Augsburg Nuernberg Ag Laufrad für Zentrifugallüfter mit axialem Eintritt und radialem Austritt.
US3221398A (en) * 1961-01-25 1965-12-07 Ruth D Mayne Method of manufacturing a turbine type blower wheel
US4363601A (en) * 1979-01-19 1982-12-14 Oy Nokia Ab Impeller in a centrifugal blower
US5336050A (en) * 1993-05-06 1994-08-09 Penn Ventilator Co. Inc. Ventilator fan device
EP1138954B1 (fr) 2000-03-30 2009-12-16 Technofan Ventilateur centrifuge
DE10310981A1 (de) * 2003-03-07 2004-09-23 Piller Industrieventilatoren Gmbh Laufrad für Gebläse
WO2005073559A1 (fr) 2004-01-23 2005-08-11 Robert Bosch Gmbh Ventilateur centrifuge

Also Published As

Publication number Publication date
EP3181912B1 (fr) 2019-09-04
ITUB20159662A1 (it) 2017-06-15

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