EP0100078B1 - Ventilateur axial - Google Patents

Ventilateur axial Download PDF

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Publication number
EP0100078B1
EP0100078B1 EP83107227A EP83107227A EP0100078B1 EP 0100078 B1 EP0100078 B1 EP 0100078B1 EP 83107227 A EP83107227 A EP 83107227A EP 83107227 A EP83107227 A EP 83107227A EP 0100078 B1 EP0100078 B1 EP 0100078B1
Authority
EP
European Patent Office
Prior art keywords
axial
intake
ventilator according
exhaust
center plane
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.)
Expired
Application number
EP83107227A
Other languages
German (de)
English (en)
Other versions
EP0100078A1 (fr
EP0100078B2 (fr
Inventor
Günter Wrobel
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.)
Ebm Papst St Georgen GmbH and Co KG
Original Assignee
Papst Motoren GmbH and Co KG
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
Family has litigation
First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=6169236&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=EP0100078(B1) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by Papst Motoren GmbH and Co KG filed Critical Papst Motoren GmbH and Co KG
Publication of EP0100078A1 publication Critical patent/EP0100078A1/fr
Publication of EP0100078B1 publication Critical patent/EP0100078B1/fr
Application granted granted Critical
Publication of EP0100078B2 publication Critical patent/EP0100078B2/fr
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/52—Casings; Connections of working fluid for axial pumps
    • F04D29/522—Casings; Connections of working fluid for axial pumps especially adapted for elastic fluid pumps
    • F04D29/526—Details of the casing section radially opposing blade tips
    • 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
    • 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
    • F04D25/0613—Units comprising pumps and their driving means the pump being electrically driven the electric motor being specially adapted for integration in the pump the electric motor being of the inside-out type, i.e. the rotor is arranged radially outside a central stator

Definitions

  • the invention relates to an axial fan, in particular a small fan of axial compactness, with a housing jacket enclosing the fan wheel, the inner contour of which is cylindrical in the region of the axial central plane and which forms a polygonal, in particular square, circumscribing the diameter of the fan wheel towards the blow-off side and towards the suction side Profile is expanded, and with a central coaxial core, which is formed by the drive motor, the hub of the fan wheel and the mounting flange for the drive motor and which has an outer ring surface tapering towards the front side of the suction side, as a result of which an inlet channel tapering in the flow direction is formed , wherein the axial length of the tapered ring surface is at least 1/3 of the length of the hub.
  • Such axial fans are preferably used for cooling in electrical and electronic devices and systems, particularly wherever very compact fan dimensions and low noise with high air performance are required.
  • the space available in such devices also limits the dimensions of the fans that can be used. As a measure to increase the performance of such fans, an increase in dimensions is therefore ruled out.
  • the housing casing is cylindrical with a small gap to the fan blades and widens to a square shape by walls that run obliquely and symmetrically to the axial center plane in the corner areas, both towards the suction side and the discharge side.
  • the housings of such devices can also be made increasingly smaller.
  • the object of the invention is therefore to provide an axial fan which has a greater performance than the known axial fans of this type, which is to be achieved without increasing the external dimensions of the known axial fans.
  • the housing shell merges from its cylindrical region into a circumferential inlet curve. This results in an expanded inlet cross section on the intake side, which only gradually becomes narrower than the flow channel section delimited by the cylindrical part of the housing shell. It is advantageous if the radius of curvature of the inlet rounding is provided to be greater than or equal to 1/3 of the distance between the axial center plane and the suction side, that is to say is chosen to be relatively large.
  • FIG. 1 designates an axial fan which, because of its small external dimensions and its compact design, is preferably used for cooling in electronic or electrical devices.
  • the fan wheel is installed in a housing jacket 2.
  • the fan blades 4 and the motor housing 3 can be seen in FIG. 1.
  • the fan shown preferably has a contour of less than 100 mm square side length and an axial length of less than 32 mm.
  • the housing jacket 2 has a partial region 5 in which it extends cylindrically and concentrically to the fan axis B. From this cylindrical area 5, the housing shell 2 merges into a square shape on the suction side as well as on the blow-off side, with 6 fastening bores 7 being made in the corner areas thus created.
  • the engine is constructed in a manner known per se.
  • the shaft 15 is fixedly connected via the bushing 11 to the motor housing 3, which is formed on the outside in one piece as a squirrel-cage rotor, the rods of which run in a manner known per se through the laminated sheets 16 of the rotor.
  • the fan blades 4 are then attached to the outer circumference of the motor housing 3 designed as a hub.
  • the interior in which the fan wheel is arranged is limited in the axial center plane A by the cylindrical region 5 of the housing shell 2, which extends to the suction side 9 over a length a 2 that is greater than half the distance a from which Axial center plane A to the intake side 9.
  • the housing casing runs in the corner areas from the axial center plane A with an inclined wall 17, so that overall there is an asymmetrical design with respect to the axial center plane A between the suction side half and the discharge side half of the axial fan.
  • the cylindrical region 5 merges into an inlet curve 18, the radius of curvature R of which is approximately one third of the distance a from the axial center plane A to the suction side 9.
  • the cylindrical region 5a extends over the entire distance between the axial center plane A and the suction side 9. This means that the performance can be achieved just as with an axial fan, whose cylindrical area 5b merges with a bevel 24 in the outer edge area to the suction side 9 (see FIG. 4), compared to the known axial fans.
  • FIG. 2 shows a circumferential round edge with a relatively large inlet radius R, this has a theoretical value of zero in the embodiment according to FIG. 3.
  • 4 shows only a small angle of expansion of the cylinder surface 5b in the region of the cone surface 24 towards the inflow side; it starts, for example, from one eighth of the axial length of the housing from the entry level 9 and has a value of approximately 60 °.
  • FIG. 6 shows a variant of the tapering ring surface 10 according to FIG. 2.
  • this is a surface which is cylindrically offset in the axial direction in the region of the closed outer rotor base with a region 65 with a reduced diameter d, with the length l 1 , which gradually changes into an area 66 with the full rotor diameter d 2 .
  • Blades 63 are butt-welded to a rotor cap 61 deep-drawn from soft magnetic metal, for example by capacitor discharge, so that a larger inlet cross-section (namely as in the case of the conical annular surface 10 of FIG. 2) is provided in the inflow direction 60.
  • a rotor pot area 65 with a reduced diameter acts in the same way as a strongly pronounced inlet cone of the rotor hub or of the flange.
  • a cylindrical part 67 of the channel wall extends from the central plane A by a length a 2 to the suction side, which is significantly greater than the remaining axial length of the channel wall between its cylindrical part and the suction opening.
  • the channel wall merges into the square corner areas with a wall 68 that extends the channel.
  • An inclined wall 68 (which is only a coaxial conical surface in special cases) can also be replaced by a wall with cylindrical surfaces, the diameter of which is gradually increased towards the exit surface, as indicated by a wall 69, so that so-called full corner pockets are formed , while in the event of a gradual transition through the sloping corner walls 68 something like a "half corner pocket is formed.
  • the ratio of the lengths a z + a 3 / 2a 1 should have a minimum value of 0.3, but preferably a value of 0.5.
  • a 3 corresponds to the distance between the central axis A and the beginning of the widening region of the duct wall on the outlet side and 2a, the total axial length of the fan.
  • the ratio a 2 + a 3 / 2a should be even larger, whereby optimal value can then be about 0.5.
  • the ratio of 1 i / 2a has a minimum value of about 0.3.
  • the housing has an outer ring wall 74, which merges into square fastening tabs, as shown in FIG. 1, as one piece with fastening webs 75 and a flange 76 and a bearing tube made of parts 77, 78, 79 educated; and that is why it is a one-piece plastic injection molded or pressed part, preferably with an enlarged inner diameter of the bearing tube in the area of bearings 72, 73 compared to the central part 78 for inserting the bearings, because the fan shown is driven by a collectorless, in particular a so-called 2- pulsating DC motor is driven. Especially when the fan is very small, it is difficult to control the electronics in the motor area, i. H. either in flange 76 or. 7, to accommodate in the area of the closed rotor bottom 71.
  • the motor can preferably be a brushless DC motor, in particular a 1- or 2-pulse motor with permanent magnetic rotor, in which the electronics for commutation are arranged in the area of the motor.
  • collectorless DC fans with 1- or 2-pulse operation there are particularly few electronic components and these are therefore inexpensive to accommodate in the drive hub of the fan. At the same time, they also generate relatively little heat, so that the bearing tube 77, 78, 79 can be made of plastic in a collectorless DC motor for driving the fan in general, but in particular in a 1- or 2-pulse operated collectorless DC motor. It has sufficient fatigue strength and maintains tolerances over a long service life because the heating caused by the motor losses and the electronics is so low.
  • the carbon storage tube can be economically very advantageously manufactured in one piece with the rest of the housing.
  • Fig. 8 shows in a similar configuration as Fig. 6 and 7 shoulder-like pockets 81 and 89 and additionally inclined corner walls 84 and 88 on the entry and exit side.
  • a transition point 85 from a corner wall 84 in on the entry side a cylindrical wall 87 is further away from the central plane A than on the exit side the point 86, in which the transition from the cylindrical wall 87 to the corner wall 88 takes place.
  • the stepped recesses, which lead to the formation of the corner pockets 81 and 89, are above all production-friendly and guarantee better dimensional accuracy of the one-piece plastic housing, which is otherwise similar to that of FIG. 7, namely in one piece including a bearing tube and consisting of plastic.
  • Fig. 9 clearly shows that a small extension into the corners on the inflow side, as drawn in Fig. 4, brings a very advantageous curve with a slightly higher pressure requirement, while at a pronounced maximum pressure, the differences disappear due to different contours of the inflow opening and in the medium pressure range, where the practical applications are, a relatively large radius of curvature of the circumferential contour (as indicated in FIG. 2) clearly brings an additional improvement.
  • the setting angle ⁇ a on the radial outside on the inflow side (again formed by the tangent to this wing edge and its angle to the entry plane) is smaller than the setting angle on the radial outside edge on the outflow side a. That is, ⁇ i is smaller than ⁇ i and ⁇ a is smaller than ⁇ a , the relationships, as shown in FIG. 10, being optimal for a fan according to FIG. 2, while in the case of FIGS. 6, 7, 8 Similar relationships apply, but advantageously ⁇ i is approximately equal to a.
  • the blade curvature is approximately that of a cylinder surface. In all these cases, the angles ⁇ i and ⁇ i continuously change into ⁇ a and ⁇ a in the radially directed course of the entry and exit edges.
  • ⁇ i , E are preferably in the range between 30 ° and 50 ° and the values for ⁇ i , ⁇ a in the range between 40 ° and 60 °, where ⁇ i is approximately equal to ⁇ a .

Landscapes

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

Claims (15)

1. Ventilateur axial, en particulier ventilateur miniature de faible encombrement axial, comportant une enveloppe de boîtier (2), qui entoure le rotor du ventilateur et dont la forme interne est cylindrique dans la région du plan médian axial (A), cette forme interne étant évasée du côté du refoulement (8) ainsi que du côté de l'aspiration (9) en présentant des zones de dégagement à chaque coin (6), de manière à réaliser un profil polygonal, en particulier carré, qui est circonscrit au diamètre du rotor du ventilateur ; le ventilateur comportant un noyau central coaxial, constitué par le moteur d'entraînement, par le moyeu du rotor et par la patte support du moteur ; ce noyau central comportant une face annulaire externe qui va en s'amincissant en direction de la face frontale d'aspiration, de manière à réaliser un canal d'entrée qui va en se rétrécissant dans le sens de l'écoulement ; la longueur axiale de la face annulaire amincie étant au moins égale à 1/3 de la longueur du moyeu ; caractérisé en ce que l'enveloppe du boîtier (2) est réalisée de manière asymétrique dans les zones des coins (6) par rapport au plan médian axial (A), et présente de part et d'autre de ce plan médian (A) une partie cylindrique (5, 5a, 5b), qui s'étend du côté-de la face d'aspiration (9) sur une distance (a2) plus forte que du côté de la face de refoulement.
2. Ventilateur axial conforme à la revendication 1, caractérisé en ce que la distance (a2) est égale au moins à la moitié de la distance (a,/2) qui existe entre le plan médian axial (A) et la face d'aspiration (9).
3. Ventilateur axial conforme à l'une des revendications 1 ou 2, caractérisé en ce que l'enveloppe du boîtier (2) présente, à l'endroit de son bord disposé du côté de la face d'aspiration (9), une partie circulaire d'entrée du profil arrondi (18) qui se raccorde à la partie cylindrique (5) de l'enveloppe..
4. Ventilateur axial conforme à la revendication 3, caractérisé en ce que le rayon de courbure (R) du profil arrondi d'entrée (18) est supérieur ou égal à 1/3 de la distance (a,) qui existe entre le plan médian axial (A) et la face d'aspiration (9).
5. Ventilateur axial conforme à l'une des revendications 1 ou 2, caractérisé en ce que la partie cylindrique (5b) de l'enveloppe du boîtier (2) est raccordée par un chanfrein (24) à chacune des zones de dégagement des coins (6) du côté de la face d'aspiration (9).
6. Ventilateur axial conforme à l'une des revendications 1 ou 2, caractérisé en ce que l'enveloppe du boîtier (2) présente une forme cylindrique (5a) sur toute la distance (a,) comprise entre le plan médian axial (A) et la face d'aspiration (9).
7. Ventilateur conforme à la revendication 1, caractérisé en ce que le moteur d'entraînement est un moteur à courant continu sans collecteur, en particulier un moteur à aimant permanent fonctionnant par une ou deux impulsions, le circuit électronique de commutation étant disposé au voisinage du moteur.
8. Ventilateur axial conforme à la revendication 7. caractérisé en ce que le boîtier parallélépipédique présente en vue axiale en plan un profil carré de moins de. 100 mm de côté, et une longueur axiale de 32 mm au maximum.
9. Ventilateur axial conforme à la revendication 1, caractérisé en ce que le noyau central présente du côté de l'entrée de l'écoulement un diamètre extérieur qui va en diminuant progressivement dans la zone de la face fermée du fond du rotor.
10. Ventilateur axial conforme à l'une des revendications 1 à 9, caractérisé en ce que le profil de la paroi interne du boîtier va en s'évasant progressivement du côté du refoulement, de manière à réaliser dans les coins des parties dégagées qui sont déportées.
11. Ventilateur axial conforme à la revendication 1, caractérisé en ce qu'il comporte, du côté de l'aspiration et/ou du refoulement, des enfoncements (81, 89) déportés, qui sont ménagés dans la zone de chaque coin de fixation dù boîtier.
12. Ventilateur axial conforme à la revendication 1, caractérisé en ce que les pales du rotor présentent du côté de l'aspiration des angles de calàge (ε1 ε2) plus faibles que les angles de calage (a;, αa) prévus du côté du refoulement ; e, et αi étant les angles de calage à l'endroit du pied de chaque pale, du côté de l'aspiration et du refoulement, respectivement, tels que déterminés par les tangentes à la surface du pied de pale et le plan d'écoulement d'aspiration ou de refoulement : alors que e, et a, sont les angles de calage de l'extrémité de chaque pale dans le sens radial, du côté de l'aspiration et du refoulement, respectivement, tels que déterminés par les tangentes à la surface de l'extrémité de la pale et le plan d'écoulement d'aspiration ou de refoulement.
13. Ventilateur axial conforme à la revendication 12, caractérisé en ce que les angles εi et εa sont compris entre 30° et 50°, les angles αi et a, étant compris entre 40° et 60°, et l'angle αi étant sensiblement égal à l'angle αa.
14. Ventilateur axial conforme à l'une des revendications 1 à 13, caractérisé en ce que le fond extérieur (61) du rotor, coaxial au noyau central, présente une face cylindrique déportée (65), raccordée par un épaulement à la partie (66) qui correspond au diamètre maximum du rotor.
15. Ventilateur axial conforme à la revendication 14, caractérisé en ce que le fond extérieur (61) du rotor est réalisé par emboutissage profond dans un matériau magnétique à faible coefficient de coercitivité.
EP83107227A 1982-07-24 1983-07-22 Ventilateur axial Expired - Lifetime EP0100078B2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3227698 1982-07-24
DE19823227698 DE3227698A1 (de) 1982-07-24 1982-07-24 Axialventilator

Publications (3)

Publication Number Publication Date
EP0100078A1 EP0100078A1 (fr) 1984-02-08
EP0100078B1 true EP0100078B1 (fr) 1987-10-21
EP0100078B2 EP0100078B2 (fr) 1993-06-30

Family

ID=6169236

Family Applications (1)

Application Number Title Priority Date Filing Date
EP83107227A Expired - Lifetime EP0100078B2 (fr) 1982-07-24 1983-07-22 Ventilateur axial

Country Status (6)

Country Link
US (1) US4734015A (fr)
EP (1) EP0100078B2 (fr)
JP (1) JPH0650119B2 (fr)
CA (1) CA1338735C (fr)
DE (2) DE3227698A1 (fr)
SG (1) SG64990G (fr)

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CN105545815A (zh) * 2016-01-21 2016-05-04 山西省安瑞风机电气有限公司 一种矿用轴流风机铜钢复合防爆叶轮筒体及其制作方法

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JP2008267176A (ja) * 2007-04-17 2008-11-06 Sony Corp 軸流ファン装置、ハウジング及び電子機器
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JP2013113128A (ja) * 2011-11-25 2013-06-10 Sanyo Denki Co Ltd 軸流ファン
JP5832052B1 (ja) * 2015-04-24 2015-12-16 山洋電気株式会社 双方向軸流ファン装置
TWI614412B (zh) * 2015-12-02 2018-02-11 建準電機工業股份有限公司 軸流式風扇及其扇輪
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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105545815A (zh) * 2016-01-21 2016-05-04 山西省安瑞风机电气有限公司 一种矿用轴流风机铜钢复合防爆叶轮筒体及其制作方法

Also Published As

Publication number Publication date
EP0100078A1 (fr) 1984-02-08
DE3227698A1 (de) 1984-01-26
JPS5977240A (ja) 1984-05-02
SG64990G (en) 1991-02-14
DE3227698C2 (fr) 1991-01-17
DE3374144D1 (en) 1987-11-26
US4734015A (en) 1988-03-29
EP0100078B2 (fr) 1993-06-30
JPH0650119B2 (ja) 1994-06-29
CA1338735C (fr) 1996-11-26

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