EP0316470B1 - Ventilateur radial avec volute interne - Google Patents

Ventilateur radial avec volute interne Download PDF

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Publication number
EP0316470B1
EP0316470B1 EP19870116970 EP87116970A EP0316470B1 EP 0316470 B1 EP0316470 B1 EP 0316470B1 EP 19870116970 EP19870116970 EP 19870116970 EP 87116970 A EP87116970 A EP 87116970A EP 0316470 B1 EP0316470 B1 EP 0316470B1
Authority
EP
European Patent Office
Prior art keywords
housing
rotor
radial
wall
radial 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.)
Expired - Lifetime
Application number
EP19870116970
Other languages
German (de)
English (en)
Other versions
EP0316470A1 (fr
Inventor
Wilhelm Reinhardt
Gerhard Ruck
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.)
Elektrobau Mulfingen and Co EBM GmbH
Original Assignee
Elektrobau Mulfingen and Co EBM GmbH
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 Elektrobau Mulfingen and Co EBM GmbH filed Critical Elektrobau Mulfingen and Co EBM GmbH
Priority to DE8787116970T priority Critical patent/DE3786171D1/de
Priority to EP19870116970 priority patent/EP0316470B1/fr
Publication of EP0316470A1 publication Critical patent/EP0316470A1/fr
Application granted granted Critical
Publication of EP0316470B1 publication Critical patent/EP0316470B1/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
    • F04D29/42—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
    • F04D29/4233—Fan casings with volutes extending mainly in axial or radially inward direction
    • 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

Definitions

  • the invention relates to a radial fan for in particular gaseous media, such as air, consisting of a housing with a substantially cylindrical peripheral wall, a front end wall, a rear end wall, an inlet opening in the front end wall and an outlet opening and from a concentrically within the housing an axis of rotation rotatably arranged radial impeller, the impeller consisting of a rear cover plate connected to a drive shaft, facing away from the inlet opening, a front cover plate axially opposite this, facing the inlet opening, and extending axially between the cover plates and essentially radially on the Radially distributed blades arranged circumferentially, the rear cover plate extending in the radial direction to the outer ends of the blades, the blades with their inner ends in the radial direction having an axial, with the inlet Opening surrounded by an inlet opening connected to the front cover plate, and wherein inside the housing in the axial direction next to the impeller, an inner spiral chamber which widens in cross-section in the direction of
  • Such a radial fan with an internal spiral is known from the literature reference "Bruno Eck, Ventilatoren, Springer-Verlag, 5th edition 1972, pages 212 and 213".
  • the spiral which is laid inwards has the consequence that the housing itself can be cylindrical.
  • the impeller of the known radial fan has both a front and a rear cover plate, each of which extends in the radial direction up to the outer ends of the blades.
  • the peripheral wall of the housing must enclose the impeller with a radial distance so that the axially sucked-in and radially accelerated or compressed medium radially flow out of the impeller and in the axial direction into the inner spiral chamber adjacent to the impeller and from there again radially or tangentially the outlet opening can flow.
  • the known radial fan presumably due to this guidance or deflection of the medium, causes a relatively high level of noise and has an unsatisfactory efficiency and a relatively flat characteristic curve.
  • Document GB-A-381 431 discloses a blower, the impeller of which has blades ending near a housing peripheral wall, but only a cover plate, namely a "rear” cover plate. There is no “front” cover plate. Furthermore, an outflow chamber is arranged on one side of the impeller, namely on the side of the rear cover disk, which is only present here, but it is not clear from the drawings and the disclosure that this is actually an "impeller" - Direction of rotation in the cross section expanding inner spiral chamber ".
  • a diffuser is arranged in this known fan between the impeller and the chamber, so that consequently the outflow chamber is not arranged directly next to the impeller.
  • Document GB-A-321 847 describes a blower, the impeller of which has a front and a rear cover plate, the spiral chamber being arranged on the side of the rear cover plate.
  • the front cover disk extends in the radial direction to the outer ends of the rotor blades, which are radially spaced apart from a housing circumferential wall, and encircles the rotor blades with an arcuate section to the level of the rear cover disk, which has a smaller diameter than the front cover disk, so that one opening in the direction of the spiral chamber is formed. For this reason, the deflection of the medium from the radial direction into the axial direction is effected here by the front cover disk which is curved in the outer peripheral region.
  • spiral chamber does not expand here in the plane parallel to the plane of rotation, but the housing wall extends obliquely to the plane of rotation, so that the chamber is only referred to as "quasi-spiral" ("quasi-volute").
  • the invention has for its object to minimize the noise, optimize the efficiency and improve the characteristic in a radial fan of the generic type with a structurally simplified structure.
  • this is achieved in that the rotor blades of the impeller with their outer ends in the radial direction and the rear cover disk with its outer circumference in the immediate vicinity of the inner surface of the end cylindrical peripheral wall of the housing, wherein the inner spiral chamber is arranged on the side of the front cover plate, and the front cover plate has a circular, axially passing into the inner spiral chamber, and wherein the inner spiral chamber of a spiral, in the axial direction of the front housing end wall is limited in the immediate vicinity of the front cover extending separating web.
  • close proximity in connection with the outer ends of the rotor blades is to be understood as the smallest possible radial distance, which enables frictionless rotation of the impeller within the housing, between the ends of the rotor blades and the peripheral wall.
  • An air flow in the radial direction should be as low as possible.
  • the distance between the outer ends of the blades and the inner surface of the peripheral wall can be up to approximately 5% of the diameter of the impeller.
  • the configuration according to the invention ensures that the medium (air) flowing in via the inlet opening in the axial direction into the region of the inlet of the impeller and then accelerated by the rotor blades in the radial direction - instead of exiting the impeller in the radial direction - now from the cylindrical one Housing peripheral wall is axially deflected back towards the front housing end wall, ie via the circular opening of the front cover plate into the inner spiral chamber arranged here.
  • the medium is consequently deflected "within” the impeller, advantageously from the circumferential wall of the housing, which represents a structurally very simple and inexpensive solution.
  • the inner spiral chamber can be formed in a particularly simple manner by the separating web, which can be molded, for example, on a housing cover which forms the front end wall.
  • the housing of the blower according to the invention is therefore very inexpensive to manufacture.
  • the configuration according to the invention creates a radial blower which, in comparison to designs known from the prior art, has a very steep characteristic curve, has good efficiency and the noise development is reduced to a minimum.
  • the radial fan according to the invention can also be made much smaller and more compact, since according to the invention a radial distance between the impeller and the peripheral wall of the housing is unnecessary.
  • FIGS. 1 to 3 show two versions, which are no longer fully encompassed by the invention, but have partial features which - alternatively or additionally - can be used in the embodiment according to FIGS. 1 to 3.
  • a radial fan 2 consists of a housing 4 with an essentially cylindrical or hollow cylindrical peripheral wall 6, a front end wall 8 and a rear end wall 10.
  • the housing 4 also has an inlet opening 12 in the front end wall 8 and an outlet opening 14.
  • inlet opening 12 and the outlet opening 14 are possible, which will be explained in more detail below.
  • a radial impeller 20 is arranged concentrically to the peripheral wall 6 and rotatable about an axis of rotation 16, which has a circular, for example a hub 21 with a drive shaft 22 connected or connectable rear cover disk 24 with substantially radially arranged, extending in the axial direction from the rear cover disk 24 forward, distributed over its circumference arranged radial rotor blades 26.
  • the impeller 20 also has a front cover plate 28 connected to the rotor blades 26 on the side axially opposite the rear cover plate 24.
  • the rotor blades 26 are curved forward, but the invention is in no way limited to this, but the impeller 20 can also have rotor blades 26 that are curved backwards or straight out.
  • the blades 26 can furthermore have a blade depth measured in the axial direction, which decreases in the radial direction from the inside to the outside (see FIG. 1) or else is constant (compare FIGS. 4 and 5).
  • the drive shaft 22 extends through the rear end wall 10 of the housing 4 and is connected to a drive motor 30 fastened to this end wall 10, which in the example shown is an external rotor motor.
  • a drive motor 30 fastened to this end wall 10, which in the example shown is an external rotor motor.
  • other types of engine are also possible.
  • the blades 26 lie with their inner ends 31 in the radial direction on the circumference of an axial inlet 32 which is circular in cross section, which has the circular inlet opening 12 of the front end wall 8 and a likewise circular inflow opening 34 of the front cover disk 28 (only in FIG. 1 4 to 4) are substantially aligned in the axial direction (axis 16).
  • the centers these openings 12 and 34 and the central axis of the inlet 32 lie on the axis of rotation 16.
  • the front cover disk 28 is consequently - due to the inflow opening 34 - in the form of an annular disk and possibly - due to the shape of the blades 26 shown in FIG. 1 - light conical.
  • an inner spiral chamber 36 is formed in the axial direction on one side of the impeller 20, namely on the side of the front cover disk 28, which widens in cross section in the direction of rotation of the impeller (arrow 38 in FIGS. 2 and 6) and into the Outlet opening 14 merges.
  • the radial fan 2 according to the invention has a diameter ratio D1 / D2 in the range from 0.2 to 0.6, in particular 0.32 in the examples shown, D1 being the diameter of the inlet 32 and D2 the outer diameter of the impeller (see FIG. 2) .
  • the blades 26 of the impeller 20 end with their outer ends 39 in the radial direction at a short distance from the inner surface 40 of the housing peripheral wall 6, ie between the ends 39 of the blades 26 and the inner wall surface 40, according to the invention, there is only a minimal one, while observing tolerances customary in production radial distance available, which is just sufficient to enable a smooth rotation of the impeller 20 within the housing 4.
  • the front cover disk 28 facing the inner spiral chamber 36 has in the axial direction an annular opening 42 opening into the inner spiral chamber 26, which is preferably formed in the area adjacent to the outer circumference of the impeller 20, ie the cover disk 28 According to the invention, the impeller 20 covers only up to the annular opening 42 in the radial direction.
  • the outlet opening 14 of the housing 4 is, according to the invention, offset in all the illustrated embodiments in the axial direction relative to the impeller 20.
  • the outlet opening 14 is designed as a blow-out nozzle 46 arranged or integrally formed in the housing peripheral wall 6, which preferably has a rectangular flow cross section.
  • the outlet connection 46 has a front wall 47, a rear wall 48 parallel to this, an upper wall 49 and a lower wall 50 parallel to this.
  • the front wall 47 is formed as an extension of the front end wall 8 of the housing 4.
  • the peripheral wall 6 of the housing 4 goes continuously into the upper wall 49 forming a tangent and over a curvature 52 into the lower wall 50.
  • the rear wall 48 forms a housing edge 54 in a transition region to the housing peripheral wall 6, it being essential to the invention that this housing edge 54 lies axially outside an axial region X (FIG. 1) defined by the axial length of the outer ends 39 of the blades 26 , which has a particularly advantageous effect on the desired noise reduction.
  • An enlargement of the inlet opening should therefore always be carried out by shifting the lower wall 50 of the outlet connector 46 or the curvature 52 in the circumferential direction or by a lateral housing extension in the region of the front end wall 8.
  • a further reduction in running noise is achieved according to the invention in that a web 56 is arranged along the housing edge 54 in the corner region between the rear wall 48 and the lower wall 50 of the blow-out connector 46, the web 56 viewed in the direction of rotation of the wheel 38 approximately after 1 / 4 to 1/3 of the length of the housing edge 54 begins and then increases steadily in its axially measured height, wherein in the region of the curvature 52 or the lower wall 50 of the outlet nozzle 46 it is its greatest height, in particular approximately 50-70% of that in the axial direction Direction measured length of the curvature 52 or the lower wall 50 of the blow-out spigot 46 (see in particular Fig. 3).
  • the inner spiral chamber 36 is formed according to the invention by a spiral-shaped separating web 60 extending from the front housing end wall 8 in the axial direction up to the immediate vicinity of the front cover disk 28.
  • the separating web 60 spirally surrounds the inlet opening 12 up to an end point 66 lying on an imaginary extension of the lower wall 50 of the blow-out connector 46 and merges here into a substantially straight web section 60a connecting the end point 66 to the starting point 64.
  • the front cover disk 28 has an annular web 70 which surrounds the inflow opening 34 and points in the direction of the front housing end wall 8. Furthermore, the front housing end wall 8 also has an annular web 72 which surrounds the inlet opening 12 but points in the direction of the inlet 32 of the impeller 20 and forms an inlet nozzle. In the embodiment according to FIGS. 1 to 3, it is now provided according to the invention that the annular web 72 of the housing end wall 8 engages axially in the area enclosed by the annular web 70 of the cover disk 28.
  • the ring webs 70, 72 can also be substantially flush with one another in the axial direction Distance.
  • the inlet opening 12 can, according to the invention, also be circular, preferably with the inlet 32 of the impeller 20 in Hole opening covering axial direction may be formed in the front end wall 8. There is consequently no ring web forming an inlet nozzle in this embodiment, so that the impeller 20 can be arranged very close to the inner surface of the front end wall 8, which advantageously leads to a further reduction in the axial overall length.
  • the outlet opening 14 is formed in the rear end wall 10 in the axial direction.
  • An analogous application of this embodiment would, in the embodiment according to the invention according to FIGS. 1 and 3, lead to the outlet opening 14 being formed in the front end wall 8 in the axial direction.
  • the blower according to the invention can be constructed in two parts from die-cast or plastic with blades made from die-cast or steel or sheet metal for applications in the hot air or gas blower area. For other applications that involve less thermal stress, it is of course also possible to use plastic impellers.

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

Claims (12)

  1. Ventilateur radial (2) en particulier pour milieux gazeux, comme par exemple l'air, constitué d'un carter (4) comportant une paroi périphérique sensiblement cylindrique (6), une paroi extrême avant (8), une paroi extrême arrière (10), une ouverture d'entrée (12) dans la paroi extrême avant (8) et une ouverture de sortie (14), ainsi que d'une roue mobile radiale (20) montée de manière concentrique à l'intérieur du carter (4) et en rotation autour d'un axe de rotation (16), la roue mobile (20) étant constituée d'un disque de recouvrement arrière (24), qui est relié à un arbre d'entraînement (22) et est opposé à l'ouverture d'entrée (12), d'un disque de recouvrement avant (28), qui fait face axialement au disque de recouvrement arrière (24) et qui est tourné vers l'ouverture d'entrée (12), ainsi que d'aubes mobiles radiales (26) qui s'étendent axialement entre les disques de recouvrement (24, 28) et qui sont réparties sensiblement radialement sur la périphérie, le disque de recouvrement arrière (24) s'étendant, dans le sens radial, jusqu'aux extrémités extérieures (39) des aubes mobiles (26), les extrémités (31) des aubes mobiles (26) situées à l'intérieur dans le sens radial entourant une entrée axiale (32) reliée à l'ouverture d'entrée (12) par l'intermédiaire d'une ouverture d'admission (34) du disque de recouvrement avant (28), et à l'intérieur du carter (4) étant formée, dans le sens axial, à côté de la roue mobile (20), une chambre à volute interne (36) dont la section transversale s'élargit dans le sens de rotation (38) de la roue mobile et qui débouche dans l'ouverture de sortie (14), caractérisé en ce que les extrémités extérieures radiales (39) des aubes mobiles (26) de la roue mobile (20) ainsi que la périphérie extérieure du disque de recouvrement arrière (24) se terminent à proximité immédiate de la surface intérieure (40) de la paroi périphérique cylindrique (6) du carter (4), la chambre à volute interne (36) se trouvant du côté du disque de recouvrement avant (28), le disque de recouvrement avant (28) comportant une ouverture annulaire (42) qui débouche axialement dans la chambre à volute interne (36), et la chambre à volute interne (36) étant délimitée par une nervure de séparation (60) en forme de volute qui s'étend dans le sens axial de la paroi extrême avant (8) du carter jusqu'à proximité immédiate du disque de recouvrement avant (28).
  2. Ventilateur radial selon la revendication 1, caractérisé en ce que l'ouverture annulaire (42) du disque de recouvrement avant (28) est formée dans la zone de ce dernier adjacente à la périphérie extérieure de la roue mobile (20).
  3. Ventilateur radial selon la revendication 1 ou 2, caractérisé en ce que le disque de recouvrement avant (28) comportant l'ouverture annulaire (42) possède un diamètre extérieur (d) qui représente de 60 % à 93 %, en particulier 81 %, du diamètre extérieur (D2) de la roue mobile (20).
  4. Ventilateur radial selon une ou plusieurs des revendications 1 à 3, caractérisé en ce que l'ouverture de sortie (14) du carter (4) est décalée axialement par rapport à la roue mobile (20) et se trouve en particulier, dans le sens axial, à l'extérieur d'une zone axiale (X) définie par la longueur axiale des extrémités extérieures (39) des aubes mobiles (26).
  5. Ventilateur radial selon une ou plusieurs des revendications 1 à 4, caractérisé en ce que l'ouverture de sortie (14) est conçue sous la forme d'une tubulure de sortie (46) qui est montée de façon sensiblement tangentielle dans la paroi périphérique (6) du carter et qui possède une section transversale d'écoulement de préférence rectangulaire.
  6. Ventilateur radial selon la revendication 5, caractérisé en ce que, à l'intérieur de la tubulure de sortie (46), dans sa zone de coin tournée axialement vers la roue mobile (20) et axialement vers l'axe de rotation (16), une nervure (56) est disposée le long d'un bord de carter (54) formé entre la tubulure de liaison (46) et la paroi périphérique (6) du carter, la hauteur, mesurée axialement, de la nervure (56) augmentant dans le sens de rotation (38) de la roue mobile (20).
  7. Ventilateur radial selon une ou plusieurs des revendications 1 à 4, caractérisé en ce que l'ouverture de sortie (14) est réalisée axialement dans l'une des parois extrêmes (8, 10) du carter.
  8. Ventilateur radial selon une ou plusieurs des revendications 1 à 7, caractérisé en ce que le disque de recouvrement avant (28) comporte un rebord annulaire (70) qui entoure l'ouverture d'admission (34) et est tourné en direction de la paroi extrême avant (8) du carter.
  9. Ventilateur radial selon une ou plusieurs des revendications 1 à 8, caractérisé en ce que la paroi extrême avant (8) du carter comporte un rebord annulaire (72) qui entoure l'ouverture d'entrée (12), qui est tourné en direction de l'entrée (32) de la roue mobile (20) et qui forme une buse d'entrée.
  10. Ventilateur radial selon la revendication 8 et 9, caractérisé en ce que le rebord annulaire (72) de la paroi extrême (8) du boîtier pénètre axialement dans la zone entourée par le rebord annulaire (70) du disque de recouvrement (28).
  11. Ventilateur radial selon la revendication 8 et 9, caractérisé en ce que les rebords annulaires (72, 70) de la paroi extrême (8) et du disque de recouvrement (28) se font face dans le sens axial avec un écartement réduit.
  12. Ventilateur radial selon l'une ou plusieurs des revendications 1 à 8, caractérisé en ce que l'ouverture d'entrée (12) est réalisée sous la forme d'un trou circulaire qui, de préférence, coïncide avec l'entrée (32) de la roue mobile (20) et qui est pratiqué dans la paroi extrême avant (8).
EP19870116970 1987-11-17 1987-11-17 Ventilateur radial avec volute interne Expired - Lifetime EP0316470B1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
DE8787116970T DE3786171D1 (de) 1987-11-17 1987-11-17 Radialgeblaese mit innenspirale.
EP19870116970 EP0316470B1 (fr) 1987-11-17 1987-11-17 Ventilateur radial avec volute interne

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP19870116970 EP0316470B1 (fr) 1987-11-17 1987-11-17 Ventilateur radial avec volute interne

Publications (2)

Publication Number Publication Date
EP0316470A1 EP0316470A1 (fr) 1989-05-24
EP0316470B1 true EP0316470B1 (fr) 1993-06-09

Family

ID=8197454

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19870116970 Expired - Lifetime EP0316470B1 (fr) 1987-11-17 1987-11-17 Ventilateur radial avec volute interne

Country Status (2)

Country Link
EP (1) EP0316470B1 (fr)
DE (1) DE3786171D1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101975192A (zh) * 2010-07-28 2011-02-16 苏州顶裕节能设备有限公司 一种叶轮前盖板

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4009869A1 (de) * 1990-03-28 1991-10-02 Mulfingen Elektrobau Ebm Radialgeblaese mit innenspirale
DE4141106C2 (de) * 1991-12-13 2001-10-04 Papst Licensing Gmbh & Co Kg Radialgebläse
DE4242474A1 (de) * 1992-12-16 1994-06-23 Sel Alcatel Ag Vorrichtung zum Fördern eines gasförmigen Mediums
DE20016769U1 (de) * 2000-09-28 2000-12-14 Papst-Motoren GmbH & Co. KG, 78112 St Georgen Radialgebläse, insbesondere für Beatmungsgeräte
CN106321512A (zh) * 2016-10-31 2017-01-11 广东威灵电机制造有限公司 叶轮和具有其的风机
CN106402020A (zh) * 2016-10-31 2017-02-15 广东威灵电机制造有限公司 叶轮和具有其的风机

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB321847A (en) * 1928-11-29 1929-11-21 James Keith & Blackman Company Improvements in or relating to centrifugal fans
US1876871A (en) * 1930-09-29 1932-09-13 H H Franklin Mfg Company Fan construction
GB381431A (en) * 1931-01-22 1932-10-06 British Thomson Houston Co Ltd Improvements in and relating to centrifgal compressors
CH219997A (de) * 1941-02-17 1942-03-15 Ventilator A G Ventilator.
US2462518A (en) * 1946-12-14 1949-02-22 Jet Heet Inc Air compressor
US3093299A (en) * 1961-05-15 1963-06-11 Trane Co Centrifugal fan
GB2057567A (en) * 1979-08-24 1981-04-01 Borg Warner Expanding scroll diffuser for radial flow impeller

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101975192A (zh) * 2010-07-28 2011-02-16 苏州顶裕节能设备有限公司 一种叶轮前盖板

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EP0316470A1 (fr) 1989-05-24
DE3786171D1 (de) 1993-07-15

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