WO2015090318A1 - Soufflante à écoulement axial à pales tournés selon un rapport de pas de pale qui diminue de façon (quasi)linéaire avec la position radiale - Google Patents

Soufflante à écoulement axial à pales tournés selon un rapport de pas de pale qui diminue de façon (quasi)linéaire avec la position radiale Download PDF

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Publication number
WO2015090318A1
WO2015090318A1 PCT/DK2013/050432 DK2013050432W WO2015090318A1 WO 2015090318 A1 WO2015090318 A1 WO 2015090318A1 DK 2013050432 W DK2013050432 W DK 2013050432W WO 2015090318 A1 WO2015090318 A1 WO 2015090318A1
Authority
WO
WIPO (PCT)
Prior art keywords
fan
hub
axis
blade
blades
Prior art date
Application number
PCT/DK2013/050432
Other languages
English (en)
Inventor
Karl Erik WIDELL
Original Assignee
Dacs A/S
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 Dacs A/S filed Critical Dacs A/S
Priority to EP13811779.1A priority Critical patent/EP3084230A1/fr
Priority to PCT/DK2013/050432 priority patent/WO2015090318A1/fr
Priority to US15/105,458 priority patent/US20160319836A1/en
Publication of WO2015090318A1 publication Critical patent/WO2015090318A1/fr

Links

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
    • F04D29/32—Rotors specially for elastic fluids for axial flow pumps
    • F04D29/34—Blade mountings
    • F04D29/36—Blade mountings adjustable
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D19/00—Axial-flow pumps
    • F04D19/002—Axial flow fans
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/32—Rotors specially for elastic fluids for axial flow pumps
    • F04D29/38—Blades
    • F04D29/384—Blades characterised by form
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/32—Rotors specially for elastic fluids for axial flow pumps
    • F04D29/38—Blades
    • F04D29/384—Blades characterised by form
    • F04D29/386—Skewed blades
    • 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
    • F04D29/52—Casings; Connections of working fluid for axial pumps
    • F04D29/54—Fluid-guiding means, e.g. diffusers
    • F04D29/541—Specially adapted for elastic fluid pumps
    • F04D29/545—Ducts

Definitions

  • the present invention relates to an axial flow fan having an advantageous design of the rotor blades.
  • Axial flow fans are well known in the art and many different designs have been proposed and manufactured in order to improve the performance of the fan, in particular with respect to generation of noise and improved power efficiency. It is an object of the present invention to provide an improved fan design to improve the efficiency of the fan.
  • R is the radial distance from the axis and to the free tip end of the blade and r is the radial distance from the axis and to the radial position.
  • Such blade has a steeper chord angle ⁇ at the region near the hub and tends to drive the core of the flow right after the rotor in a so-called forced vortex, which appear to improve the efficiency of the fan.
  • the angle ⁇ deviates less that 4°, preferably less than 2° from the curve defined by the equation.
  • the angle ⁇ deviates less that 4°, preferably less than 2° from the curve defined by the equation.
  • an axial flow fan comprising a hub rotatable about an axis, an annular shroud extending concentric with said axis in a radial distance from said hub, a plurality of fan blades connected at a root end to said hub and having a free tip end extending radially towards said shroud, fan driver coupled to said hub and arranged for driving the rotation of said hub around the axis, wherein the angle ⁇ between a direction of rotation of the blades and the chord of the blade at all positions along the radial extent of the blade substantially follows the curve defined as
  • an axial flow fan comprising a hub rotatable about an axis, an annular shroud extending concentric with said axis in a radial distance from said hub, a plurality of fan blades connected at a root end to said hub and having a free tip end extending radially towards said shroud, fan driver coupled to said hub and arranged for driving the rotation of said hub around the axis, wherein the blades are designed so that the fan when in operation at nominal operating conditions generates a fluid flow in the immediate vicinity after the blades which comprises a core flow that substantially is a forced vortex flow where the tangential flow speed component is proportional with the radial distance from the axis.
  • the existence of such core flow is readily detectable by means of standard fluid flow measurement techniques, such as hot wire anemometry, laser-doppler velocimetry or particle image velocimetry.
  • the core flow extends preferably to a radial distance of at least 0.2 times the radial distance from the axis to the tip of blades, preferably the core flow extends in the range of 0.2 to 0.3 times said radial distance.
  • the fluid flow in the immediate vicinity after the blades outside the core flow is preferably substantially a free vortex flow where the tangential flow speed component is inversely proportional with the radial distance from the axis to the radial position, whereas the axial flow speed component is substantially constant.
  • the inner radius of the annular shroud is in the range of 600 to 1500 millimetres.
  • the radius of the hub is preferably in the range of 50 to 75 millimetres which surprisingly has shown to improve the efficiency of the fan considerably, probably due to the reduced disturbance of the wake of the hub.
  • a fan according to the present invention preferably comprises a diffuser arranged concentric with said axis at a downstream position of the annular shroud.
  • the diffuser has a conical shape with a diffusion angle in the range of 2 to 15° to the axis of rotation of the rotor, preferably in the range of 6 to 10°.
  • a fan according to the present invention comprises an inlet part provided with a bellmouth arranged concentric with said axis at an upstream position of the annular shroud.
  • an axial flow fan comprising a hub rotatable about an axis, and at least one fan blade connected at a root end to said hub and having a free tip end extending radially away from said axis, the hub comprising a seating part allowing the blade or blades to be arranged in a plurality of blade pitch angles and blade locking part for locking the blade pitch angle of the at least one blade into a specific blade pitch angle, wherein said locking part is designed to lock said blade into one specific blade pitch angle only.
  • a loose locking pin is inserted into one of a plurality of openings in the blade root or in the seating part in order to lock the blade pitch in one of a plurality of possible pitch angles.
  • the fan comprises one locking part for each of the blades, and in a particularly preferred embodiment, the blades each comprises a recess cooperating with a corresponding pin of the locking part.
  • Fig. 1 is a longitudinal schematic cross-section of an axial flow fan
  • Fig. 2a shows the tangential flow speed of a fan designed according to the invention
  • Fig. 2b shows the axial flow speed of a fan designed according to the invention
  • Fig. 3 shows a blade of an axial flow fan according to the invention
  • Fig. 4 illustrates a cross-section of a blade together with the flow direction, the direction of blade movement and the angle ⁇ between the blade chord and the direction of movement
  • Fig. 5 is a perspective view of a hub part, three blades and three locking parts for an axial flow fan according to an aspect of the present invention.
  • Fig. 6 shows three different designs of the locking parts of Fig. 5. DETAILED DESCRIPTION OF EMBODIMENTS OF THE PRESENT INVENTION
  • the axial flow fan 1 of the present invention may be equipped with any convenient number of blades 2.
  • a fan 1 having three blades 2 is shown, but it is generally preferred that the rotor 5 of the fan comprises from 3 to 6 blades.
  • the axial flow fan 1 as illustrated in Fig. 1 comprises a number of blades 2 connected to a hub 3.
  • the rotor 5, i.e. the hub 3 and the blades 2 is rotated about an axis 4 by means of a motor (not shown) arranged in the hub 3 or next to the hub 3 and connected thereto by means of a drive arrangement, e.g. a belt drive.
  • the rotor 5 is arranged inside a cylindrical shroud 6 which is concentric arranged about the axis 4 to that there is a clearance between the tip 7 of the blades 2 and the shroud 6.
  • the rotation of the rotor 5 drives a flow of air axially through the fan 1 in the direction of the arrow A in Fig. 1.
  • the flow path through the fan 1 is illustrated by streamlines 8 indicated in Fig. 1.
  • the shroud 6 is preceded by an inlet part 9 arranged upstream of the shroud, i.e. in the direction against the driven flow A, where the inlet part 9 also is concentric with the axis 4 and comprises a bellmouth to smoothen the flow at the inlet part 9 in order to avoid separation of the flow.
  • the passage of the air flow through the rotor 5 causes a pressure increase which is further increased by regained part of the as kinetic energy present in of the air flow immediately after the rotor due to the axial velocity component by means of a diffuser 10 arranged downstream of the shroud 6 and concentric with the axis 4.
  • the diffuser 10 has a conical shape with an diffusion angle of 8.5° to the centre line, i.e. to the axis 4 of rotation of the rotor 5.
  • the blades 2 are attached by their root end 11 to the hub 3, preferably in a manner discussed later.
  • the air is accelerated in the inlet part 9 from rest far upstream of the fan 1 to the flow condition immediately before the rotor 5.
  • the design of the blades 2 of the fan 1 has the aim and task of forming a rotor 5 which is characterised in that it during operation of the fan 1 generates an air flow immediately after the air flow passage of the rotor 5, which is a combination of two so-called Beltrami flows, i.e. cylindrical flows with constant total enthalpy, see e.g. Michael H. Vavra, Aero-Thermodynamics and Flow in Turbomachines, John Wiley & Sons, Inc. 1960.
  • the design principle according to the present invention causes the change in total enthalpy and thereby the work performed by the blades 2 of the rotor 5 on the air flow to be substantially constant over the whole cross-section of the rotor 5 which is advantageous for the efficiency of the rotor 5.
  • a forced vortex flow at the core of the flow field after the rotor 5 preferably with a core radius r c in the range of 0.2 to 0.3 the maximum tangential speed in the wake of the rotor 5 is reduced as well as the force of the whirl formed after the hub 3 which have a disadvantageous effect on regaining kinetic energy in the downstream diffuser 10.
  • the blades of a fan may be designed by the use of standard fan design tools when design parameters as fan diameter, flow rate and rotational speed of the rotor.
  • a cross section of a fan blade 2 is shown in Fig. 4 with indication of the leading edge 12 of the blade 2 as well as the trailing edge 13 and the chord line 14 extending there between, the length of the chord of the blade 2 being the distance between the leading edge 12 and the trailing edge 13. The blade 2 is moved in the direction indicated as M on Fig.
  • the Flow is designed to be 45000 m 3 /h, the nominal rotational speed n is 425 rpm and the radius R of the rotor 5 is 1.5 m.
  • the condition of the air is taken to be a temperature of 20 °C, a pressure of 101300 Pa and a relative humidity of 80%.
  • the first five columns of the table provide the parameters of the blade 2 as found by standard design tools, whereas the last two columns are the chord angles ⁇ found by means of equation 1 and equation 2, respectively.
  • the Flow is designed to be 16000 m 3 /h, the nominal rotational speed n is 970 rpm and the radius R of the rotor 5 is 0.5 m.
  • the condition of the air is taken temperature of 20 °C, a pressure of 101300 Pa and a relative humidity of
  • the Flow is designed to be 22500 m 3 /h, the nominal rotational speed n is 950 rpm and the radius R of the rotor 5 is 0.5 m.
  • the condition of the air is taken to be a temperature of 20 °C, a pressure of 101300 Pa and a relative humidity of 80%. r/R R ⁇ Chord Profile ⁇ Eq. (1) ⁇ Eq. (2)
  • the blades 2 are at the root end 11 equipped with a projection 15 that allows the individual blade 2 to be seated in a blade seating opening 17 of the seating part 16 at any pitch angle of the blade 2 as desired, the projections 15 being rotatable in the U-shaped seating openings 17.
  • the blade root protections 15 being equipped with a recess (not visible) designed for cooperating with a pin 20 having a rectangular cross-section, the pin 20 being extending from the body of a locking part 18 which is suited to the inserted into the blade seating opening 17 when the blade root projection 15 is in place so as to lock the pitch angle of the blade 2 to a specific blade pitch angle defined by the locking part 18.
  • Fig. 6 is shown three different locking parts 18a, 18b, 18c where the pin 20a, 20b, 20c are arranged at different positions to define different pitch angles of the blade 2.
  • the locking parts 18a, 18b, 18c are provided with side tracks 19 to accommodate the edges of the blade seating opening 17 of the seating part 16 of the hub 3.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

Soufflante (1) à écoulement axial comprenant un moyeu (3), une enveloppe annulaire (6) s'étendant de manière concentrique avec l'axe (4) du moyeu (3) et une pluralité de pales (2) de soufflante reliées par une extrémité d'emplanture (11) audit moyeu (3) et possédant une extrémité de pointe libre (7) s'étendant radialement vers ladite enveloppe (6), les pales (2) sont conçues de sorte que la soufflante (1), quand elle tourne dans des conditions de fonctionnement nominales, produise un écoulement de fluide à proximité directe après les pales (2) qui comprend un écoulement central qui est sensiblement un écoulement à tourbillon forcé où la composante de vitesse d'écoulement tangentielle (c2, u) est proportionnelle à la distance radiale (r) par rapport à l'axe (4). L'invention présente des équations pour définir l'angle de corde θ des pales (2).
PCT/DK2013/050432 2013-12-17 2013-12-17 Soufflante à écoulement axial à pales tournés selon un rapport de pas de pale qui diminue de façon (quasi)linéaire avec la position radiale WO2015090318A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
EP13811779.1A EP3084230A1 (fr) 2013-12-17 2013-12-17 Soufflante à écoulement axial à pales tournés selon un rapport de pas de pale qui diminue de façon (quasi)linéaire avec la position radiale
PCT/DK2013/050432 WO2015090318A1 (fr) 2013-12-17 2013-12-17 Soufflante à écoulement axial à pales tournés selon un rapport de pas de pale qui diminue de façon (quasi)linéaire avec la position radiale
US15/105,458 US20160319836A1 (en) 2013-12-17 2013-12-17 Axial flow fan with blades twisted according to a blade pitch ratio that decreases (quasi) linearly with the radial position

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/DK2013/050432 WO2015090318A1 (fr) 2013-12-17 2013-12-17 Soufflante à écoulement axial à pales tournés selon un rapport de pas de pale qui diminue de façon (quasi)linéaire avec la position radiale

Publications (1)

Publication Number Publication Date
WO2015090318A1 true WO2015090318A1 (fr) 2015-06-25

Family

ID=49880346

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DK2013/050432 WO2015090318A1 (fr) 2013-12-17 2013-12-17 Soufflante à écoulement axial à pales tournés selon un rapport de pas de pale qui diminue de façon (quasi)linéaire avec la position radiale

Country Status (3)

Country Link
US (1) US20160319836A1 (fr)
EP (1) EP3084230A1 (fr)
WO (1) WO2015090318A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DK201670645A1 (en) * 2016-08-25 2018-01-29 Dacs As Improved wing for an axial flow fan
WO2018206380A1 (fr) 2017-05-08 2018-11-15 Dacs A/S Système d'alimentation électrique pour soufflerie de ventilation

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2016023117A1 (fr) * 2014-08-13 2016-02-18 Sectar Solutions Inc. Ventilateur de plafond centrifuge
DE102014226288A1 (de) * 2014-12-17 2016-06-23 Ziehl-Abegg Se Axialventilator

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4569632A (en) * 1983-11-08 1986-02-11 Airflow Research And Manufacturing Corp. Back-skewed fan
US4900229A (en) * 1989-05-30 1990-02-13 Siemens-Bendix Automotive Electronic Limited Axial flow ring fan
WO1993005275A1 (fr) * 1991-08-30 1993-03-18 Airflow Research And Manufacturing Corporation Ventilateur a biais vers l'avant, et a inclinaison et a cambrage dans le sens de la corde
US5520515A (en) * 1995-05-23 1996-05-28 Bailsco Blades & Casting, Inc. Variable pitch propeller having locking insert
WO2002038962A2 (fr) * 2000-11-08 2002-05-16 Robert Bosch Corporation Ventilateur axial a rendement eleve et adapte a l'entree d'air
WO2005066504A1 (fr) * 2004-01-12 2005-07-21 Siemens Vdo Automotive Inc. Ventilateur basse pression a ecoulement eleve

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Publication number Priority date Publication date Assignee Title
US5244347A (en) * 1991-10-11 1993-09-14 Siemens Automotive Limited High efficiency, low noise, axial flow fan
AU1177495A (en) * 1993-11-12 1995-05-29 Penn Ventilator Co. Inc. Air moving system with optimized air foil fan blades
US5730583A (en) * 1994-09-29 1998-03-24 Valeo Thermique Moteur Axial flow fan blade structure
US5769607A (en) * 1997-02-04 1998-06-23 Itt Automotive Electrical Systems, Inc. High-pumping, high-efficiency fan with forward-swept blades
KR100332539B1 (ko) * 1998-12-31 2002-04-13 신영주 축류팬
US7249931B2 (en) * 2002-03-30 2007-07-31 University Of Central Florida Research Foundation, Inc. High efficiency air conditioner condenser fan with performance enhancements

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4569632A (en) * 1983-11-08 1986-02-11 Airflow Research And Manufacturing Corp. Back-skewed fan
US4900229A (en) * 1989-05-30 1990-02-13 Siemens-Bendix Automotive Electronic Limited Axial flow ring fan
WO1993005275A1 (fr) * 1991-08-30 1993-03-18 Airflow Research And Manufacturing Corporation Ventilateur a biais vers l'avant, et a inclinaison et a cambrage dans le sens de la corde
US5520515A (en) * 1995-05-23 1996-05-28 Bailsco Blades & Casting, Inc. Variable pitch propeller having locking insert
WO2002038962A2 (fr) * 2000-11-08 2002-05-16 Robert Bosch Corporation Ventilateur axial a rendement eleve et adapte a l'entree d'air
WO2005066504A1 (fr) * 2004-01-12 2005-07-21 Siemens Vdo Automotive Inc. Ventilateur basse pression a ecoulement eleve

Non-Patent Citations (2)

* Cited by examiner, † Cited by third party
Title
MICHAEL H. VAVRA: "ero- Thermodynamics and Flow in Turbomachines", 1960, JOHN WILEY & SONS, INC.
See also references of EP3084230A1

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DK201670645A1 (en) * 2016-08-25 2018-01-29 Dacs As Improved wing for an axial flow fan
DK179200B1 (en) * 2016-08-25 2018-01-29 Dacs As Improved wing for an axial flow fan
WO2018036598A1 (fr) * 2016-08-25 2018-03-01 Dacs A/S Ventilateur à flux axial à torsion de pale optimisée à proximité du moyeu de roue
WO2018206380A1 (fr) 2017-05-08 2018-11-15 Dacs A/S Système d'alimentation électrique pour soufflerie de ventilation

Also Published As

Publication number Publication date
EP3084230A1 (fr) 2016-10-26
US20160319836A1 (en) 2016-11-03

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