EP3193022B1 - Ventilateur centrifuge - Google Patents

Ventilateur centrifuge Download PDF

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Publication number
EP3193022B1
EP3193022B1 EP16151037.5A EP16151037A EP3193022B1 EP 3193022 B1 EP3193022 B1 EP 3193022B1 EP 16151037 A EP16151037 A EP 16151037A EP 3193022 B1 EP3193022 B1 EP 3193022B1
Authority
EP
European Patent Office
Prior art keywords
curvature
centrifugal fan
fan
section
radius
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.)
Active
Application number
EP16151037.5A
Other languages
German (de)
English (en)
Other versions
EP3193022A1 (fr
Inventor
Halil Kartal
Oktay Hancerli
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.)
Silverline Endustri ve Ticaret AS
Original Assignee
Silverline Endustri ve Ticaret AS
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 Silverline Endustri ve Ticaret AS filed Critical Silverline Endustri ve Ticaret AS
Priority to DK16151037.5T priority Critical patent/DK3193022T3/da
Priority to EP16151037.5A priority patent/EP3193022B1/fr
Priority to PL16151037.5T priority patent/PL3193022T3/pl
Publication of EP3193022A1 publication Critical patent/EP3193022A1/fr
Application granted granted Critical
Publication of EP3193022B1 publication Critical patent/EP3193022B1/fr
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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
    • F04D29/40—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
    • 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
    • F04D29/282—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for fans or blowers the leading edge of each vane being substantially parallel to the rotation axis
    • F04D29/283—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for fans or blowers the leading edge of each vane being substantially parallel to the rotation axis rotors of the squirrel-cage type

Definitions

  • the present invention relates generally to a centrifugal fan which is intended to be used in extractor hoods.
  • the present invention is particularly related to an improved structure of a centrifugal fan in order to increase energy efficiency in extractor hoods.
  • a centrifugal fan is a mechanical device for moving air or other gases. These fans increase the speed of air stream with the rotating impellers. They use the kinetic energy of the impellers or the rotating blade to increase the pressure of the air/gas stream which in turn move them against the resistance caused by ducts, dampers and other components. Centrifugal fans accelerate air radially, changing the direction of the airflow.
  • Centrifugal fan structures are designed by taking into account four important factors which are volumetric flow rate, pressure, power and noise. Said centrifugal fans provide very different structures in order to improve these factors.
  • centrifugal fans are consisted of a fan housing, an impeller, inlet and outlet ducts, a drive shaft and a drive mechanism.
  • the impeller is linked directly to the shaft of an electric motor.
  • the motor's rotational speed determines the impeller speed.
  • There are three types of impellers whose blades are arranged in there different ways such as forward-curved, backward-curved or radial.
  • the centrifugal fan uses the centrifugal power supplied from the rotation of impellers to increase the kinetic energy of air/gases.
  • the impellers rotate, the gas particles near the impellers are thrown off from the impellers, and then moves into the fan casing. Therefore, the kinetic energy of gas is measured as pressure because of the system resistance offered by the casing and duct.
  • the gas is then guided to the exit via outlet ducts. After the gas is thrown off, the gas pressure in the middle region of the impellers decreases. The gas from the impeller eye rushes in to normalize this. This cycle repeats and therefore the gas can be continuously transferred.
  • volute tongue has an important effect in order to increase the speed of air/gas stream which causes the increase in energy efficiency. Therefore, in order to reach the best energy efficiency in these centrifugal ventilation fans, manufacturers test different volute tongue angles in the centrifugal ventilation fans.
  • One of the studies done in this field is expressed in the utility model document CN202581616 .
  • Said document discloses a dehumidifier comprising a shell, a snail shaped fan, an air inlet, an air outlet and a snail tongue angle.
  • the snail tongue angle is determined between 20-40° in order to improve the performance of the dehumidifier.
  • Another patent document which discloses a centrifugal fan is DE2556614 .
  • Said centrifugal fan expresses the volute tongue angle between 25-65°.
  • Other prior art centrifugal fans are known from EP1375925 A2 and EP1701041 A2 .
  • the present invention aims to provide a centrifugal fan in order to overcome the deficiencies in the prior studies done in this field as well as to provide a centrifugal fan with more energy efficiency.
  • the centrifugal fan of the invention generates lower noise while operating.
  • the present invention is related to a centrifugal fan (1), in particular a snail type centrifugal fan (1), particularly for extractor hoods.
  • Said centrifugal fan (1) structure is intended to be used particularly, but not exclusively, in the ventilation systems for extractor hoods for evacuation of fumes, vapors, or other air-like gases mostly from domestic environments.
  • the centrifugal fan (1) of the present invention comprises two separate housing parts (2) which can be coupled to each other in a connection plane K in order to protect the inner parts of the centrifugal fan (1).
  • said housing parts (2) can be produced by plastic materials.
  • One of the housing parts (2) is not shown in the figures, while the other which comprises a motor body (3) of the centrifugal fan (1) is presented in Figs. 1 and 2 .
  • Said motor body (3) is mounted to the housing part (2) so as to be able to rotate axially and is located substantially in the middle of said housing part (2).
  • said housing parts (2) are preferably arranged in a substantially symmetrical manner with respect to the connection plane K.
  • said centrifugal fan (1) preferably comprises two radial fan impellers (4) which are connected to each other concentrically in a connection plane L. Said radial fan impellers (4) are mounted substantially into the middle of the housing part (2) around the motor body (3), coaxial with the rotation of the motor body (3).
  • the centrifugal fan (1) of the invention is constructed such that the connection planes K and L are substantially in alignment in order to provide symmetry in the centrifugal fan (1) when the housing parts (2) are coupled to each other.
  • outlet (5) for evacuation of the air-like gases in the centrifugal fan (1).
  • Said outlet (5) evacuates the air-like gases substantially in the direction of (y) which is indicated in the figures, and perpendicular to the rotation of the motor body (3).
  • Each housing part (2) comprises a structure in semi-cylindrical form in order to define the outlet (5) and throat section (6) of the housing part (2).
  • the housing parts (2) are coupled to each other in the connection plane K, corresponding parts of said throat section (6) are also coupled to each other in a fluid-tight manner and form a cylindrical outlet (5).
  • Said centrifugal fan (1) sucks the air-like gases towards the inside by rotation of said radial fan impellers (4) by using kinetic energy.
  • an air inlet section comprising some holes to ensure air flow inside the centrifugal fan (1).
  • Said air inlet section is defined on another housing part which is not shown in the figures.
  • the centrifugal fan structure (1) is configured such that when the two housing parts (2) are coupled to each other in the connection plane K, said air inlet section faces with the open side (7) of the radial fan impellers (4). Consequently, the air-like gas is drawn inside via the rotation of the radial fan impellers (4) driven by the motor body (3).
  • the open side (7) of the radial fan impeller (4) comprises a main opening (8) preferably in a cylindrical form being also coaxial with the rotation axis of the motor body (3).
  • said housing part (2) of the centrifugal fan structure (1) also comprises some protrusions (9) along the connection plane K in order to provide the tight connection between the two housing parts (2), when they are coupled in the connection plane K and twisted around said connection plane K.
  • the housing part (2) also comprises a connection seat (11) which is able to couple with the corresponding seat of the other housing part in the state of engagement.
  • the centrifugal fan (1) comprises a tongue section (12) in the region of the outlet (5), which defines the throat section (6) as conventionally known in the snail type fans.
  • Said tongue section (12) causes the cross-section of the air flow channel to be narrowed locally, upon which the said cross section expands again above tongue section (12), and in this expanded region in close proximity to the outlet (5), the pressure of the air flow considerably drops.
  • Said tongue section (12) facilitates also a connection between the two housing parts (2) with the connection spots (13) in the state of engagement. According to new regulations all over the world, it is required and highly preferred that extractor hoods have the A+ energy efficiency which is hardly achieved by way of the conventional snail fans.
  • the curvatures in said tongue section (12) are of vital importance for increasing the energy efficiency, and it is found that by optimizing the curvatures in the tongue section (12) of the throat, the required level of energy efficiency can be obtained without the undue burden of changing overall design of the conventional snail type fans.
  • said tongue section (12) comprises the curvature B, which plays an important role in behavior of the air flow in the centrifugal fan (1).
  • the curvature B forms the extreme point of the tongue section (12) in the horizontal direction (x).
  • the impeller (4) rotates in counter-clockwise direction according to Figs. 3-5 , for instance, the curvature B convexly facing the rigorous air flow causes a disturbance which deteriorates a laminar flow regime and causes local vortexes to be formed around the periphery of the tongue section (12).
  • the conventional snail type fans comprise a tongue section with a sharp or smoothly curved structure of the above type and therefore are not responsive to the drawbacks such as deterioration of the laminar flow and creating vortexes. It is known that irregular flow regimen in a snail type fan causes energy consumption to increase per volume of the air discharged through the outlet.
  • the said tongue section (12) defined by the horizontal width H comprises a further curvature D convexly formed through the throat of the outlet (5) which is connected to the first curvature B by way of a longitudinal surface C. It is thereby ensured that the air flow impinging upon said first curvature B neighboring the impeller (4), flows over the surface C and arrives to curvature D whereby said airflow expands smoothly through the area defined by the width G. It is also unexpectedly found that the surface C, if it is formed as a concavely extending curvature, advantageously ensures preserving of the laminar flow through the curvature D and outlet (5).
  • the curvature B mentioned above is realized with a circle whereby its radius (r B ) is perfectly designed in the range of 2,9 mm to 3,6 mm.
  • the closest vertical distance (A) between the center of the circle belonging to curvature B and the connection plane L of the impellers (4) is preferably arranged inbetween 7-9 mm.
  • the transverse distance between the center of the circle belonging to curvature B and the center of the impeller (4) is designated as x b
  • the longitudinal distance between the center of the circle belonging to curvature B and the center of the impeller (4) is designated as y b .
  • the x b /y b ratio is preferably determined inbetween 0,6 and 0,8.
  • the surface C is preferably formed as a concave curvature which is realized with a circle where its radius (r c ) is advantageously arranged inbetween 55 and 70 mm.
  • the circle of the curvature B is tangent to the circle of the curvature C.
  • the curvature D can be envisaged with a circle whereby its radius (r d ) is advantageously arranged inbetween 10 mm and 25 mm.
  • the circle of the curvature D is again tangent to the circle of curvature C.
  • the inventors are of the opinion that the condition of r c being substantially bigger than r d ensures the fact that curvature D does not disturb the air flow and instead a smooth passage of the flow is guaranteed through the outlet (5) defined by the width G.
  • the results of the simulation as demonstrated in Fig. 5 verify that a perfect flow regime is obtained by the arrangement comprising at least two curvatures (B, D) and a surface C extending therebetween substantially in vertical direction.
  • the tongue section (12) further comprises a surface S which is tangential to the circle of the curvature D.
  • Said surface S is preferably formed as a straight line which is inclined and has an angle with the horizontal axis (x) which is 10 to 15°.
  • the horizontal distance H between the imaginary plane P which is tangential to the curvature B and the imaginary plane T which is tangential to one end of the throat section (6) is preferably determined between 70 mm and 85 mm in the axis of (x).
  • the horizontal distance G between the vertical plane defined by the center of the circle (D) and the imaginary plane T which is tangential to one end of the outlet section (5) is determined between 55 mm and 62 mm in the axis of (x).
  • the vertical distance F between the point where surface S is tangential to the circle of the curvature D and the uppermost horizontal line of the outlet section (5) is advantageously determined between 35 mm and 45 mm in the vertical axis of (y).
  • the present invention presents extractor hoods comprising the centrifugal fan (1) of the present invention, and also a method for producing the same comprising placing of said centrifugal fan (1) into a hood structure.
  • Table I the simulation results of the prototypes produced in consideration of the values mentioned above are presented. Said values are obtained according to the EN 61591 and EN 60704 standards.

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

Claims (10)

  1. Ventilateur (1) centrifuge du type escargot comprenant deux parties de boîtier (2) qui peuvent être accouplées l'une à l'autre dans un plan de connexion K, un corps de moteur (3) monté dans l'une des parties de boîtier (2), au moins une roue (4) de ventilateur radial montée autour du corps de moteur (3) qui est coaxiale avec l'axe de rotation du corps de moteur (3), et une section languette (12) dans la région d'une sortie (5) de la partie de boîtier (2) définissant une section gorge (6) rétrécissant la coupe transversale de passage d'air dans un axe horizontal (x) dans lequel ladite section languette (12) comprend ;
    - une première courbure (B) formée de manière convexe avoisinant la roue (4) formant un point extrême dans une direction horizontale (x) dans le volume intérieur du ventilateur (1) centrifuge, et
    - une courbure (D) supplémentaire formée de manière convexe à travers la sortie (5) à une position supérieure de la première courbure (B) par rapport à l'axe vertical (y) du ventilateur (1) centrifuge,
    moyennant quoi, ladite première courbure (B) s'étend vers la seconde courbure (D) à travers une surface (C) qui est tangentielle par rapport aux première et seconde courbures (B, D), et ladite surface (C) comprend une structure formée de manière concave s'étendant entre les première et seconde courbures (B, D).
  2. Ventilateur (1) centrifuge selon la revendication 1, dans lequel le rayon de la première courbure (B) est entre 2,9 mm et 3,6 mm.
  3. Ventilateur (1) centrifuge selon la revendication 1, dans lequel le rayon de la seconde courbure (D) est entre 10 mm et 25 mm.
  4. Ventilateur (1) centrifuge selon la revendication 1, dans lequel le rayon de la surface (C) formée de manière concave (rc) est plus grand que le rayon de la seconde courbure (D) (rd).
  5. Ventilateur (1) centrifuge selon la revendication 4, dans lequel le rayon de la surface (C) formée de manière concave (rc) est entre 55 mm et 70 mm.
  6. Ventilateur (1) centrifuge selon la revendication 1 dans lequel la section languette (12) comprend en outre une surface (S) qui est tangentielle par rapport au cercle de la courbure D, ladite surface (S) étant formée comme une ligne droite qui est inclinée et ayant un angle de 10° à 15° par rapport à l'axe horizontal (x) du ventilateur (1) centrifuge.
  7. Ventilateur (1) centrifuge selon la revendication 1 dans lequel la distance horizontale (G) dans l'axe horizontal (x) entre le plan vertical défini par le centre du cercle appartenant à la courbure (D) et le plan imaginaire T qui est un plan vertical défini par une extrémité de la section sortie (5) est de 55 mm à 62 mm.
  8. Ventilateur (1) centrifuge selon la revendication 1 dans lequel le ventilateur comprend une distance transversale (xb) entre le centre du cercle appartenant à la courbure B et le centre de la roue (4), et une distance longitudinale (yb) entre le centre du cercle appartenant à la courbure B et le centre de la roue (4), moyennant quoi le rapport xb/yb est de 0,6 à 0,8.
  9. Hotte à extraction comprenant un ventilateur (1) du type escargot selon la revendication 1.
  10. Procédé pour produire une hotte à extraction selon la revendication 9 comprenant le placement d'un ventilateur (1) du type escargot selon la revendication 1 dans la structure de hotte.
EP16151037.5A 2016-01-13 2016-01-13 Ventilateur centrifuge Active EP3193022B1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
DK16151037.5T DK3193022T3 (da) 2016-01-13 2016-01-13 Centrifugalventilator
EP16151037.5A EP3193022B1 (fr) 2016-01-13 2016-01-13 Ventilateur centrifuge
PL16151037.5T PL3193022T3 (pl) 2016-01-13 2016-01-13 Wentylator odśrodkowy

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP16151037.5A EP3193022B1 (fr) 2016-01-13 2016-01-13 Ventilateur centrifuge

Publications (2)

Publication Number Publication Date
EP3193022A1 EP3193022A1 (fr) 2017-07-19
EP3193022B1 true EP3193022B1 (fr) 2022-05-25

Family

ID=55085603

Family Applications (1)

Application Number Title Priority Date Filing Date
EP16151037.5A Active EP3193022B1 (fr) 2016-01-13 2016-01-13 Ventilateur centrifuge

Country Status (3)

Country Link
EP (1) EP3193022B1 (fr)
DK (1) DK3193022T3 (fr)
PL (1) PL3193022T3 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN114046270B (zh) * 2021-12-15 2024-08-27 广东美的白色家电技术创新中心有限公司 离心风机和电器设备
WO2025129883A1 (fr) * 2023-12-20 2025-06-26 海信空调有限公司 Climatiseur

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2556614A1 (de) 1975-12-16 1977-06-23 Mulfingen Elektrobau Ebm Spiralgehaeuse fuer luefter
IT250953Y1 (it) * 2000-05-11 2003-10-22 Zephyr S R L Convogliatore aria applicabile anche per elettrodomestici cappe dacucina in plastica o metallo alimentato da motore elettrico
JP2004019635A (ja) * 2002-06-20 2004-01-22 Sanden Corp 遠心送風機
JP2006242554A (ja) * 2005-02-04 2006-09-14 Matsushita Electric Ind Co Ltd 空気調和機
ITPD20060446A1 (it) * 2006-12-06 2008-06-07 Ln 2 Srl Socio Unico Collettore a chiocciola, particolarmente per ventilatori da impiegarsi in cappe aspiranti
CN202581616U (zh) 2012-03-26 2012-12-05 宁波奥克斯空调有限公司 一种除湿机

Also Published As

Publication number Publication date
PL3193022T3 (pl) 2022-10-10
EP3193022A1 (fr) 2017-07-19
DK3193022T3 (da) 2022-08-29

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