EP3330545B1 - Ventilateur centrifuge - Google Patents

Ventilateur centrifuge Download PDF

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Publication number
EP3330545B1
EP3330545B1 EP17201511.7A EP17201511A EP3330545B1 EP 3330545 B1 EP3330545 B1 EP 3330545B1 EP 17201511 A EP17201511 A EP 17201511A EP 3330545 B1 EP3330545 B1 EP 3330545B1
Authority
EP
European Patent Office
Prior art keywords
motor
stator
side wall
radial blower
conveying space
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
EP17201511.7A
Other languages
German (de)
English (en)
Other versions
EP3330545A1 (fr
Inventor
SIlvia Quattrone
Fortunato Grippo
Fabio TANTALO
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.)
Elica SpA
Original Assignee
Elica SpA
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Filing date
Publication date
Application filed by Elica SpA filed Critical Elica SpA
Priority to PL17201511T priority Critical patent/PL3330545T3/pl
Publication of EP3330545A1 publication Critical patent/EP3330545A1/fr
Application granted granted Critical
Publication of EP3330545B1 publication Critical patent/EP3330545B1/fr
Active legal-status Critical Current
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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
    • F04D25/00—Pumping installations or systems
    • F04D25/02—Units comprising pumps and their driving means
    • F04D25/08—Units comprising pumps and their driving means the working fluid being air, e.g. for ventilation
    • F04D25/082—Units comprising pumps and their driving means the working fluid being air, e.g. for ventilation the unit having provision for cooling the motor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D25/00—Pumping installations or systems
    • F04D25/02—Units comprising pumps and their driving means
    • F04D25/06—Units comprising pumps and their driving means the pump being electrically driven
    • F04D25/0606—Units comprising pumps and their driving means the pump being electrically driven the electric motor being specially adapted for integration in the pump
    • 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
    • F04D29/58—Cooling; Heating; Diminishing heat transfer
    • F04D29/5806—Cooling the drive system

Definitions

  • the present invention relates to a radial blower for moving air, e.g. for gas water heaters for domestic sanitary use with thermal powers up to 35 kW.
  • the known radial blowers comprise an impeller rotationally arranged within a substantially toroidal-shaped housing with two side walls and a peripheral wall.
  • An inlet aperture is formed in one of the two side walls arranged in a radially inner, but not necessarily central position of the housing.
  • a tangential portion with an outlet aperture is formed in the peripheral wall.
  • the impeller is rotational by means of an electric motor located outside the housing and connected to the side wall opposite to the inlet aperture.
  • a driving shaft extends from the rotor of the motor through a passage aperture in the side wall inside the housing in which it integrally connects to the impeller.
  • the electric motor comprises its own housing or motor support with a stator seat which accommodates the motor stator and with one or more bearings to support the driving shaft and the rotor of the motor.
  • the motor support is externally screwed to the side wall of the housing.
  • dampers interposed between the motor support and the impeller housing e.g. rubber or silicone bushes, are envisaged.
  • Radial blowers of the prior art are disclosed for example in documents EP 0 408 221 A2 , WO 2016/059776 A1 , DE 10 2013 204 138 A1 or US 2013/0101451 A1 .
  • the radial blower comprises:
  • Making the motor support in one piece with the second side wall of the housing further reduces misalignments between the motor and the housing and respective vibrations (noise).
  • one or more through cooling apertures are formed in the second side wall, extending radially outside of the rotor seat and radially superimposed with the electric motor, in particular with the stator, so as to achieve a cooling communication between the stator (on the outer side of the second side wall) and the conveying space (on the inner side of the second side wall).
  • an electronic control circuit of the electric motor is configured to truncate the current peaks in the windings of the stator, or, in other words, to supply a truncated amplitude wave current to the stator windings, as shown in figure 6 compared with a non-truncated current pattern, shown in figure 7 .
  • a radial blower indicated as a whole by reference numeral 1, comprises an impeller 2 arranged in rotational manner in a conveying space 3 defined inside a housing 4.
  • the housing 4 has a substantially toroidal shape with a first side wall 5 and a second side wall 6 opposite to the first side wall 5, and a peripheral wall 7.
  • An inlet aperture 8 is formed in the first side wall 5 for the gas or air to be conveyed in a radially inner, but not necessarily central position of housing 4.
  • a substantially tangential portion 9, which defines an outlet 10 for gas or air, is formed in the peripheral wall 7.
  • An electric motor 11 is arranged outside the conveying space 3.
  • the motor 11 is adapted to make the impeller 2 rotate by means of a driving shaft 12, which extends through a passage 13 formed in the second side wall 6 from outside the housing 4 into the conveying space 3, in which it connects, in rotationally integral manner, to the impeller 2.
  • a motor support 14 forms a stator seat 15, in which a stator 16 of the motor 11 is received and locked, and a rotor seat 17 for the rotary support of a rotor 18 of the motor 11 and of the driving shaft 12.
  • the motor support 14 is formed directly (or preferably in one piece) with the second side wall 6 and axially protrudes into the conveying space 3 so that the conveying space 3 at least partially envelops the stator 16 and the rotor seat 17.
  • the second side wall 6 comprises a radially outer portion 19, which is substantially flat and perpendicular to the rotation axis 20 of the motor 11 and of the impeller 2.
  • the motor support 14 protrudes, with respect to the radially outer portion 19, axially into the conveying space 3, by an axial length 21 of at least one fourth of a (maximum) axial height 22 of the conveying space 3.
  • the ratio of the axial length 21 to the maximum axial height 22 is in the range from 0.25 to 0.5, advantageously from 0.35 to 0.44, even more advantageously the ratio is about 0.39.
  • the motor support portion 14 which protrudes into the conveying space 3 has a tapered shape towards a free end, preferably formed by an axially more external first portion 23 and adjacent to the radially outer portion 19, and an axially more internal second portion 24, which is radially tapered with respect to the first portion 23, e.g. at a step which forms an intermediate portion 25, which may be planar and perpendicular with respect to the rotation axis 20 or inclined with respect to the rotation axis by an inclination angle from 45° to 135°, preferably from 75° to 105°.
  • the axial length 26 of the first portion 23 is either equal to or greater than the axial length 27 of the second portion 24.
  • the first portion 23 and the second portion 24 both have an outer cylindrical or truncated-cone shape which is concentric to the rotation axis 20.
  • the first portion 23 accommodates at least one portion of the stator 16 and preferably also at least one part of the rotor 18, while the second portion 24 internally forms at least one part of the rotor seat 17, e.g. a seat for a bearing.
  • the motor support 14 invades the conveying space in such a manner not to negatively interfere with the conveying of the air or gas.
  • the maximum axial height 20 denotes the distance between the inner surface of the radially outer portion 19 of the second side wall 6 and an opposite inner surface of a radially outer portion 28 of the first lateral wall 5, also preferably planar and perpendicular to the axis of rotation 20.
  • the maximum axial width 44 of the blades 30 of the impeller 2 is less than 2/3 of the maximum axial height 22 of the conveying space 3, preferably the ratio between the maximum axial width 44 of the blades 30 and the maximum axial height 22 of the conveying space 3 is in the range of 1/3 to 2/3, advantageously from 2/5 to 3/5, even more advantageously from 0.45 to 0.6.
  • the impeller 2, and particularly the blades 30, are positioned adjacent to the first side wall 5 and have an axial width which is smaller than the axial width of the outlet aperture 10, which may be equal to the maximum axial height 22 of the conveying space 3.
  • the impeller does not need to be as wide as the housing, but in order to obtain an optimum output flow and for the need for connection compatibility, the outlet aperture must have a predetermined width, which can be greater than the axial width of the impeller 2. Precisely in these conditions it is advantageous to make the impeller 2 with axial dimensions smaller than the axial dimensions of the outlet aperture 10 and to occupy at least part of the space not occupied by the impeller 2 with the motor 11.
  • the impeller 2 comprises a support wall 29 which connects the blades 30 of the impeller 2 to the driving shaft 12 and which defines the impeller 2 on the side of the second side wall 6, and is shaped as an circular disc extended from the driving shaft 12 to a region that is radially external to the motor support 14 or at least to its first portion 23.
  • one or more through cooling apertures 31 are formed in the second side wall 6, positioned and extending radially outside the rotor seat 17 and radially superimposed with the position of the electric motor 11, in particular with the stator 16, so as to provide a cooling communication between the stator 16 (arranged on the outer side of the second side wall 6) and the conveying space 3 (formed on the inner side of the second side wall 6).
  • a circumferential air flow along the peripheral wall 7 caused by the rotation of the impeller 2 creates a vacuum at the cooling apertures 31, which in turn determines at least one part of the partial cooling flow for the cooling of the stator 16 of the motor 11, and also of the power components of an electronic control board 33 connected to the stator 16.
  • the cooling aperture or apertures 31 are formed in the intermediate portion 25 of the motor support 14, e.g. a circumferential sequence of apertures 31 (e.g. circular, triangular or trapezoidal) alternating with radial connection ribs 34.
  • the cooling of the motor 11 through the cooling apertures 31 advantageously makes it possible to use a motor 11 without own coolant fan and therefore of further reduced axial dimensions.
  • the electronic control circuit 33 of the electric motor 11 is configured to truncate the current peaks in the stator windings, or in other words, to supply the stator windings with a wave current having truncated amplitude at the current peaks.
  • the reduction of torque ripple makes it possible, for example, to accommodate the stator 16 and/or the rotor 18 in the respective housings 15, 17 of the motor support 14 without the interposition of damping layers or elements, and to keep the noise of the blower 1 low in all cases.
  • the electric motor is a unilateral bearing motor and the rotor seat 17 forms a first bearing seat 17' and a second bearing seat 17" which are coaxial.
  • the bearing seats 17', 17" may be formed one facing towards the outside and the other facing towards the inside of the conveying space 3. This positioning facilitates the mounting of the motor and allows the use of fewer components to fix the rotating part.
  • the bearings are preferably smooth cylindrical annular bearings or rolling bearings.
  • the stator seat 15 is formed in an annular wall 35, preferably circular and continuous.
  • the annular wall 35 defines a shoulder 35 which forms an axial abutment surface for the stator 16 and one or more side surfaces 37, which achieve the engagement by clamping of the stator 16, preventing transverse displacements in the axial direction.
  • the stator 16 may comprise one or more snap-coupling portions which interact with respective counter-coupling portions of the motor support 14 to facilitate the provisional or definitive positioning and/or connection thereof.
  • the stator 16 may further form a plurality of fixing holes 38 aligned with corresponding fixing holes 39 formed in the second side wall 6 and/or with corresponding fixing holes 40 formed in a protective lid 41 (possibly provided with cooling apertures or cooling slots) and/or with fixing holes 42 of an electronic control board 33 for fixing the motor 11, by means of screws, to the housing 4.
  • the fixing holes 39 in the second side wall 6 are arranged so that the position of the electronic board 33 may be varied as required.
  • the housing 4 is made of plastic material.
  • the housing 4 may comprise two half-shells made separately, e.g. by molding, and successively joined, e.g. by snap-fastening or by means of a plurality of hooks 43 which can be moved in a snapping manner into respective fastening positions.
  • a damping layer or element (not shown), e.g. made of rubber, may be provided interposed between the rotor 18 and the motor support 14 and/or between the stator 16 and the motor support 14.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Magnetic Bearings And Hydrostatic Bearings (AREA)

Claims (14)

  1. Ventilateur centrifuge (1), comprenant :
    - un logement (4) avec une première paroi latérale (5), une seconde paroi latérale (6) opposée à la première paroi latérale et une paroi périphérique (7) qui définissent ensemble un espace d'acheminement (3), dans lequel la première paroi latérale (5) forme une ouverture d'entrée (8) et la paroi périphérique (7) forme une ouverture de sortie (10),
    - une roue (2) logée dans l'espace d'acheminement (3),
    - un moteur électrique (11),
    - un support de moteur (14) qui forme un logement de stator (15) dans lequel un stator (16) du moteur (11) est logé, et un siège de rotor (17) pour le support rotatif d'un arbre de moteur (12) raccordé à un rotor (18) du moteur (11),
    caractérisé en ce que le moteur électrique (11) est agencé en dehors de l'espace d'acheminement (3) et le support de moteur (14) est directement formé par la seconde paroi latérale (6) et fait saillie axialement dans l'espace d'acheminement (3) de sorte que l'espace d'acheminement (3) enveloppe au moins partiellement le stator (16) et le siège de rotor (17).
  2. Ventilateur centrifuge (1) selon la revendication 1, dans lequel la seconde paroi latérale (6) comprend une portion radialement extérieure (19) qui est sensiblement plate et perpendiculaire à l'axe de rotation (20) de la roue (2), dans lequel le support de moteur (14) fait saillie, par rapport à la portion radialement extérieure (19), dans l'espace d'acheminement (3) d'une longueur axiale (21) d'au moins un quart d'une hauteur axiale maximum (22) de l'espace d'acheminement (3).
  3. Ventilateur centrifuge (1) selon la revendication 2, dans lequel le rapport de la longueur axiale (21) à la hauteur axiale maximum (22) est dans la plage de 0,25 à 0,5, avantageusement de 0,35 à 0,44, même plus avantageusement le rapport est d'environ 0,39.
  4. Ventilateur centrifuge (1) selon l'une quelconque des revendications précédentes, dans lequel la portion de support de moteur (14) qui fait saillie dans l'espace d'acheminement (3) forme une première portion (23) axialement plus extérieure et une seconde portion (24) axialement plus intérieure qui est radialement effilée par rapport à la première portion (23), et un échelon qui forme une portion intermédiaire (25) qui est perpendiculaire par rapport à l'axe de rotation (20) ou inclinée par rapport à l'axe de rotation (20) avec un angle d'inclinaison de 75° à 105°.
  5. Ventilateur centrifuge (1) selon la revendication 4, dans lequel la longueur axiale (26) de la première portion (23) est égale à ou supérieure à la longueur axiale (27) de la seconde portion (24).
  6. Ventilateur centrifuge (1) selon la revendication 4 ou 5, dans lequel la première portion (23) et la seconde portion (24) présentent chacune une forme extérieure cylindrique ou tronconique qui est concentrique à l'axe de rotation (20), et la première portion (23) reçoit au moins une partie du stator (16), alors que la seconde portion (24) forme intérieurement au moins une partie du siège de rotor (17), en particulier un siège pour un palier.
  7. Ventilateur centrifuge (1) selon l'une quelconque des revendications précédentes, dans lequel la roue (2) comprend une paroi de support (29) qui raccorde des pales (30) de la roue (2) à l'arbre de moteur (12) et qui délimite la roue (2) sur le côté de la seconde paroi latérale (6), ladite paroi de support (29) étant formée comme un disque circulaire s'étendant depuis l'arbre menant (12) jusqu'à une région qui est radialement extérieure par rapport à une portion (23, 24, 25) du support de moteur (14) faisant saillie dans l'espace d'acheminement (3).
  8. Ventilateur centrifuge (1) selon l'une des revendications précédentes, dans lequel une ou plusieurs ouvertures de refroidissement traversantes (31) sont formées dans la seconde paroi latérale (6), lesdites ouvertures de refroidissement traversantes (31) étant positionnées et s'étendant radialement à l'extérieur du siège de rotor (17) et superposées radialement avec la position du stator (16) du moteur électrique (11), dans lequel lesdites ouvertures de refroidissement (31) fournissent une communication de refroidissement entre le stator (16) et l'espace d'acheminement (3).
  9. Ventilateur centrifuge (1) selon la revendication 8, dans lequel les ouvertures de refroidissement (31) forment une séquence circonférentielle des ouvertures (31) s'alternant avec des nervures de liaison radiales (34).
  10. Ventilateur centrifuge (1) selon la revendication 8, dans lequel le moteur (11) ne présente pas de propre ventilateur de refroidissement autre que la roue (2).
  11. Ventilateur centrifuge (1) selon l'une quelconque des revendications précédentes, dans lequel un circuit de commande électronique (33) du moteur électrique (11) est configuré de sorte à tronquer les pics de courant dans les enroulements du stator (16).
  12. Ventilateur centrifuge (1) selon l'une quelconque des revendications précédentes, dans lequel le stator (16) et le rotor (18) sont supportés dans le support de moteur (14) sans l'interposition de couches ou d'éléments d'amortissement.
  13. Ventilateur centrifuge (1) selon l'une quelconque des revendications précédentes, dans lequel le stator (16) comprend une ou plusieurs portions de couplage par enclenchement qui interagissent avec des portions de contre-couplage respectives du support de moteur (14) pour faciliter le positionnement et/ou la connexion de celui-ci.
  14. Ventilateur centrifuge (1) selon l'une quelconque des revendications précédentes, dans lequel le stator (16) forme une pluralité de trous de fixation (38) alignés sur des trous de fixation (39) correspondants formés dans la seconde paroi latérale (6) et sur des trous de fixation (40) correspondants formés dans un couvercle protecteur (41), et sur des trous de fixation (42) d'un panneau de commande électronique (33) du moteur (11) pour la fixation, au moyen de vis, du moteur (11) au logement (4), dans lequel les trous de fixation (39) dans la seconde paroi latérale (6) sont agencés de sorte que la position du panneau électronique (33) puisse être variée comme requis.
EP17201511.7A 2016-11-30 2017-11-14 Ventilateur centrifuge Active EP3330545B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PL17201511T PL3330545T3 (pl) 2016-11-30 2017-11-14 Wentylator promieniowy

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
IT102016000121296A IT201600121296A1 (it) 2016-11-30 2016-11-30 Soffiatrice radiale

Publications (2)

Publication Number Publication Date
EP3330545A1 EP3330545A1 (fr) 2018-06-06
EP3330545B1 true EP3330545B1 (fr) 2021-09-01

Family

ID=58994984

Family Applications (1)

Application Number Title Priority Date Filing Date
EP17201511.7A Active EP3330545B1 (fr) 2016-11-30 2017-11-14 Ventilateur centrifuge

Country Status (3)

Country Link
EP (1) EP3330545B1 (fr)
IT (1) IT201600121296A1 (fr)
PL (1) PL3330545T3 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP4202229A1 (fr) * 2021-12-21 2023-06-28 Andreas Stihl AG & Co. KG Conduit d'air de refroidissement sur une soufflante électrique

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2234012A (en) * 1989-07-14 1991-01-23 Ibm Dc motor driven centrifugal fan
US9574568B2 (en) * 2011-10-20 2017-02-21 Henkel IP & Holding GmbH Double inlet centrifugal blower with a solid center plate
DE102013204138A1 (de) * 2013-03-11 2014-09-11 BSH Bosch und Siemens Hausgeräte GmbH Lagerschild für einen Gebläsemotor eines Radialgebläses einer Dunstabzugshaube
JP5957712B1 (ja) * 2014-10-14 2016-07-27 パナソニックＩｐマネジメント株式会社 遠心送風機およびそれを備えた自動車

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP4202229A1 (fr) * 2021-12-21 2023-06-28 Andreas Stihl AG & Co. KG Conduit d'air de refroidissement sur une soufflante électrique

Also Published As

Publication number Publication date
PL3330545T3 (pl) 2022-02-07
IT201600121296A1 (it) 2018-05-30
EP3330545A1 (fr) 2018-06-06

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