EP0450272A2 - Ventilateur radial avec volute interne - Google Patents

Ventilateur radial avec volute interne Download PDF

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Publication number
EP0450272A2
EP0450272A2 EP91100984A EP91100984A EP0450272A2 EP 0450272 A2 EP0450272 A2 EP 0450272A2 EP 91100984 A EP91100984 A EP 91100984A EP 91100984 A EP91100984 A EP 91100984A EP 0450272 A2 EP0450272 A2 EP 0450272A2
Authority
EP
European Patent Office
Prior art keywords
housing
fan according
radial fan
radial
impeller
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.)
Granted
Application number
EP91100984A
Other languages
German (de)
English (en)
Other versions
EP0450272B1 (fr
EP0450272A3 (en
Inventor
Wilhelm Reinhardt
Horst Voss
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
Publication of EP0450272A2 publication Critical patent/EP0450272A2/fr
Publication of EP0450272A3 publication Critical patent/EP0450272A3/de
Application granted granted Critical
Publication of EP0450272B1 publication Critical patent/EP0450272B1/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
    • F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D17/08—Centrifugal pumps
    • F04D17/16—Centrifugal pumps for displacing without appreciable compression
    • 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 present invention relates to a radial fan for conveying in particular gaseous media, consisting of a housing with a peripheral wall, a front and a rear end wall, an inlet opening in the front end wall and a blow-out opening in the region of the peripheral wall, as well as one within the housing around a Rotary axis rotatably arranged radial impeller, which has a rear cover disk connected to a drive shaft with essentially radial radial vanes extending in the axial direction from the rear cover disk in the direction of the front end wall, and one axially with the rotor blades on the rear cover disk Has opposite side connected, approximately perpendicular to the axis of rotation, front cover plate with an inflow opening arranged in the region of the housing inlet opening, wherein within the housing on the in the axial direction of the front cover plate turned side next to the impeller an inner spiral chamber is formed in the direction of the impeller, widening in the direction of impeller rotation and merging into the blow-out opening.
  • the present invention has for its object to improve the generic radial fan so that a high pressure and a steep pressure / volume flow characteristic can be achieved.
  • this is achieved in that the front cover disk of the impeller merges in its outer circumferential region via a shell-like curved transition region, seen in the axial section, into an outer annular web which extends approximately axially in the direction of the inner spiral chamber.
  • the rear cover disk of the impeller facing the inner spiral chamber has such a small outer diameter that it is arranged without overlap for the axial projection of the opening of the inner spiral chamber.
  • the medium to be delivered can advantageously flow from the impeller in the axial direction over the entire opening width of the inner spiral chamber. The flow is practically loss-free in this area as well.
  • the impeller delimited in the radial direction by the outer annular web of the front cover disk approximately completely covers the axial projection of the inner spiral chamber.
  • the two opening cross sections lie opposite one another in the axial direction, as a result of which a maximum cross section is available for the flow of the medium.
  • the front cover disk also merges in the area of its inflow opening via an arc-shaped area, seen in axial section, into an inner annular web which extends approximately radially in the direction of the housing inlet opening and surrounds the inflow opening. This also results in a low-loss deflection of the medium from the axial into the radial direction in this area.
  • a very steep pressure / volume flow characteristic can be achieved, so that in the event of a pressure change, for example a change in a chimney pressure, the volume flow of the medium required is only subjected to minor changes. This advantageously makes it unnecessary to readjust the speed of a drive motor, ie to adapt the volume flow to the new pressure conditions.
  • the radial fan according to the invention is therefore particularly suitable for use as a so-called "gas fan” for gas-fired boiler systems.
  • the efficiency of such boiler systems can be increased.
  • the relatively high flow resistances within the boiler systems are advantageously overcome due to the high pressure reached.
  • 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 furthermore has an axial inlet opening 12 in the front end wall 8 and one in to the peripheral wall 6 open discharge opening 14 approximately tangential direction.
  • a radial impeller 20 is arranged within the housing 4 concentrically to the peripheral wall 6 and rotatable about an axis of rotation 16, which has a circular, e.g. Has a rear cover disk 24 connected to a drive shaft 22 via a hub 21, with radial rotor blades 26 arranged essentially radially and extending forward in the axial direction from the rear cover disk 24 and distributed over their circumference.
  • the impeller 20 also has a front cover disk 28 connected to the rotor blades 26 on their side axially opposite the rear cover disk 24.
  • the rotor blades 26 are curved forward, which advantageously ensures a high delivery rate with low running noise.
  • the invention is in no way limited to this, but the impeller 20 can also have backward curved or straight running blades 26.
  • 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 or is essentially constant.
  • 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 is preferably a collectorless DC motor.
  • a drive motor 30 fastened to this end wall 10, which is preferably a collectorless DC 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 and which is substantially aligned with the circular inlet opening 12 of the front end wall 8 in the axial direction (axis 16).
  • the front cover plate 28 has a likewise circular inflow opening 34, which in the exemplary embodiment shown has a somewhat larger diameter than the inlet opening 12, so that the blades 26 extend with their inner ends 31 inwards beyond the front cover plate 28 (see FIG. 3 and 4).
  • the center points of the openings 12 and 34 and the center 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.
  • a housing wall 10a which extends from the rear end wall 10 and extends axially away from the impeller 20 and a housing wall which adjoins this and extends radially outwards 10b (see in particular FIGS. 2 and 3) an inner spiral chamber 36 is formed, which is in the direction of rotation of the impeller (Arrow 38 in FIGS. 2 and 4) expanded in cross section and merges into the blow-out opening 14.
  • the axial housing wall 10a according to FIG. 2 runs approximately in a spiral.
  • the housing 4 is formed in two parts, the peripheral wall 6 with the front end wall 8 forming a housing front part 42 and the rear end wall 10 with the housing walls 10a and 10b forming a housing cover 44.
  • the housing cover 44 is detachably connected to the housing front part 42; Further details will be explained in the following.
  • the blow-out opening 14 of the housing 4 is also offset from the impeller 20 in the axial direction due to the axial offset of the inner spiral chamber 36 with respect to the impeller 20.
  • the blow-out opening 14 is in the housing peripheral wall 6 i.w. Tangentially arranged or integrally formed blow-out nozzle 46, which preferably has a rectangular flow cross section.
  • the blow-out connector 46 has a front end wall 48 which is perpendicular to the blow-out direction (arrow 47 in FIG. 2) and which extends like a flange beyond the blow-out cross-section or blow-out opening 14 and has fastening holes 49.
  • the front cover disk 28 of the impeller 20 goes in its outer circumferential area via a shell-like curved transition area 52, as seen in the axial section shown, into an approximately axial direction in the direction of FIG Inner spiral chamber 36 extending outer ring web 54 over.
  • this outer ring web 54 already ends in front of the radial edges of the rotor blades 26 facing the inner spiral chamber 36.
  • the ring web 43 extends axially completely over the outer end edges of the radial rotor blades 26. It is only essential that the end of the ring web 54 points approximately in the axial direction, ie in the direction of the inner spiral chamber 36, so that the medium is deflected well from the radial into the axial direction.
  • the rear cover plate 24 of the impeller 20 has such a small outside diameter that it is completely free of overlap with the opening cross section of the inner spiral chamber 36 that faces the impeller 20 axially.
  • the rear cover disk 24 does not protrude with its outer circumference into the area of the inner spiral chamber 36, so that the medium to be conveyed advantageously has an optimal, i.e. practically loss-free deflection can flow into the inner spiral chamber 36.
  • the impeller 20 delimited in the radial direction by the outer ring web 54 of the front cover disk 28 has an outer diameter such that it essentially completely covers the largest diameter of the inner spiral chamber 36.
  • the front cover disk 28 has an inner ring web 56 which surrounds the inflow opening 34 and extends approximately axially in the direction of the housing inlet opening 12, the cover disk 28 advantageously again in this inner ring web 56 via an arcuate region 58, seen in axial section transforms.
  • the hub 21 of the rear cover disk 24 tapers from the cover disk 24 in the axial direction, in particular in cross-section approximately in an arc shape, specifically in a concave manner.
  • This configuration in conjunction with the arcuate region 58 and the inner annular web 56 of the front cover plate 28, contributes to a particularly good flow guidance for the medium to be conveyed.
  • the impeller 20, including the front cover disk 28 and the rear cover disk 24 with the hub 21, is made in one piece from plastic.
  • the outer diameter of the rear cover disk 24 is at least slightly smaller than the inner diameter of the inflow opening 34 or of the inner annular web 56 of the front cover disk 28. In this way, a simple demolding of the plastic molded part is possible, in that the molds only need to be pulled apart axially.
  • the front end wall 8 of the housing 4 has an intake port 60 which surrounds the inlet opening 12 and extends axially away from the impeller 20.
  • the inner annular web 56 of the front cover disk 28 ends only a short distance in front of the intake manifold 60.
  • the intake manifold 60 is shaped on the inside in such a way that there is a continuous transition between the inner annular web 56 and the intake manifold 60 , ie between the inlet opening 12 and the inflow opening 34 results. This also contributes to a low flow resistance and thus to the desired, steep characteristic curve.
  • the housing 4, ie the housing front part 42, is expediently located in the transition region between the front end wall 8 and the circumferential wall 6 are adapted at a short distance approximately to the shell-like course of the front cover plate 28.
  • the housing cover 44 is detachably, but preferably also connected to the front housing part 42 in a gas-tight manner.
  • the housing cover 44 has for this purpose a circumferential, axial groove 62, into which the housing peripheral wall 6 of the housing front part 42 engages with its end edge 66 with the interposition of a seal 64.
  • a seal ring or a sealing cord made of an elastic material is suitable as the seal 64, for example.
  • the radial blower 2 according to the invention is particularly suitable for so-called “closed systems”, the radial blower sucking in air via a suction pipe that is tightly connected to the suction nozzle 60. A gaseous fuel is then mixed in or in front of the radial fan.
  • This gas / air mixture reaches a burner chamber via a line connection gas-tightly connected to the outlet port 46 and is burned here.
  • the exhaust gases - depending on the delivery rate of the radial fan - are pressed through a heat exchanger and discharged via an exhaust pipe.
  • each interlocking connection 70 has a spring-elastic locking arm 72 which extends from the housing cover 44 axially over the peripheral wall 6 of the housing 4 or the housing front part 42 and which has a locking edge 74 with a locking edge 74 radial engagement 76 of the circumferential wall 6 engages behind in a form-locking manner.
  • the locking edge 74 is formed in the illustrated embodiment by an opening edge of a particularly rectangular locking opening 78 of the locking arm 72.
  • the radial lugs 76 of the circumferential wall 6 each have a ramp inclined surface 80 on their side facing the housing cover 44 (FIG. 3), so that when the housing cover 44 is placed on the housing front part 52, the latching arms 72 are resiliently bent outwards via the ramp inclined surfaces 80 until they engage (snap in) the radial lugs 76 with their locking edges 74.
  • the hub 21 of the rear cover disk 24 is connected in a rotationally fixed manner to the drive shaft 22 via a radially arranged grub screw 82.
  • the hub 21 can also be connected in a rotationally fixed manner to the drive shaft 22, for example via a latching connection.
  • the motor 30 is designed as a brushless DC motor.
  • this has the advantage that speeds> 3000 rpm are readily possible, and on the other hand, due to the motor characteristic curve, a possible change in the load on the motor also results in only a slight change in speed. So this also has a positive influence on the desired steep characteristic of the radial fan.
  • the housing 4 can consist of plastic.
  • the housing 4 is made of metal.
  • the housing front part 42 is preferably made of die-cast aluminum.
  • the housing cover 44 is expediently made of a deep-drawn sheet, preferably a fire-aluminum sheet (FAL sheet), educated. Because of these materials, the radial fan 2 according to the invention is particularly well suited for conveying fuel gas / air mixtures, since so-called deflagrations can occur with such media.
  • FAL sheet fire-aluminum sheet
  • FIG. 5 shows an example of a pressure / volume flow characteristic curve diagram, in which the steep characteristic curve of the radial fan according to the invention is designated by A, while the letter B denotes a flatter characteristic curve of a conventional fan, shown in dash-dot lines. From this diagram it can be seen very clearly that with a certain pressure change ⁇ p in the radial fan according to the invention there is an extraordinarily small change ⁇ V in the volume flow (m3 / h). In contrast, with the same pressure change ⁇ p in a conventional blower (characteristic curve B), a much larger change in volume flow ⁇ V 'occurs.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
EP91100984A 1990-03-28 1991-01-25 Ventilateur radial avec volute interne Expired - Lifetime EP0450272B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4009869A DE4009869A1 (de) 1990-03-28 1990-03-28 Radialgeblaese mit innenspirale
DE4009869 1990-03-28

Publications (3)

Publication Number Publication Date
EP0450272A2 true EP0450272A2 (fr) 1991-10-09
EP0450272A3 EP0450272A3 (en) 1991-12-04
EP0450272B1 EP0450272B1 (fr) 1994-09-21

Family

ID=6403190

Family Applications (1)

Application Number Title Priority Date Filing Date
EP91100984A Expired - Lifetime EP0450272B1 (fr) 1990-03-28 1991-01-25 Ventilateur radial avec volute interne

Country Status (2)

Country Link
EP (1) EP0450272B1 (fr)
DE (2) DE4009869A1 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0546508A1 (fr) * 1991-12-13 1993-06-16 Papst Licensing GmbH Ventilateur radial
EP1361367A2 (fr) * 2002-05-08 2003-11-12 Lg Electronics Inc. Turbosoufflante et un conditionneur d' air avec une telle soufflante
DE202005004180U1 (de) * 2005-03-14 2006-07-27 Ebm-Papst Landshut Gmbh Radialgebläse
CN106884804A (zh) * 2015-12-16 2017-06-23 株式会社电装 离心式鼓风机

Citations (8)

* 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
US2240653A (en) * 1939-09-30 1941-05-06 Westinghouse Electric & Mfg Co Fan
FR1244749A (fr) * 1959-02-26 1960-10-28 Sulzer Ag Chemise d'usure pour enveloppes de ventilateurs
US3638470A (en) * 1969-06-06 1972-02-01 Gen Electric Method of making a fan
GB1416882A (en) * 1972-03-01 1975-12-10 Hotpoint Ltd Tumbler type dryers
FR2335714A1 (fr) * 1975-12-17 1977-07-15 Webasto Werk Baier Kg W Roue de ventilateur, notamment roue de soufflante a air chaud pour appareil de chauffage de vehicule
FR2340509A1 (fr) * 1976-02-04 1977-09-02 Petz Elektro Waerme Techn Ventilateur chauffant pourvu d'une machine soufflante axiale
EP0316470A1 (fr) * 1987-11-17 1989-05-24 ebm Elektrobau Mulfingen GmbH & Co. Ventilateur radial avec volute interne

Patent Citations (8)

* 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
US2240653A (en) * 1939-09-30 1941-05-06 Westinghouse Electric & Mfg Co Fan
FR1244749A (fr) * 1959-02-26 1960-10-28 Sulzer Ag Chemise d'usure pour enveloppes de ventilateurs
US3638470A (en) * 1969-06-06 1972-02-01 Gen Electric Method of making a fan
GB1416882A (en) * 1972-03-01 1975-12-10 Hotpoint Ltd Tumbler type dryers
FR2335714A1 (fr) * 1975-12-17 1977-07-15 Webasto Werk Baier Kg W Roue de ventilateur, notamment roue de soufflante a air chaud pour appareil de chauffage de vehicule
FR2340509A1 (fr) * 1976-02-04 1977-09-02 Petz Elektro Waerme Techn Ventilateur chauffant pourvu d'une machine soufflante axiale
EP0316470A1 (fr) * 1987-11-17 1989-05-24 ebm Elektrobau Mulfingen GmbH & Co. Ventilateur radial avec volute interne

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0546508A1 (fr) * 1991-12-13 1993-06-16 Papst Licensing GmbH Ventilateur radial
DE4141106C2 (de) * 1991-12-13 2001-10-04 Papst Licensing Gmbh & Co Kg Radialgebläse
DE4143663B4 (de) * 1991-12-13 2007-03-29 Papst Licensing Gmbh & Co. Kg Radialgebläse
EP1361367A2 (fr) * 2002-05-08 2003-11-12 Lg Electronics Inc. Turbosoufflante et un conditionneur d' air avec une telle soufflante
JP2003328991A (ja) * 2002-05-08 2003-11-19 Lg Electron Inc ターボファン及びこれを用いた空気調和機
EP1361367A3 (fr) * 2002-05-08 2004-08-18 Lg Electronics Inc. Turbosoufflante et un conditionneur d' air avec une telle soufflante
US7191613B2 (en) 2002-05-08 2007-03-20 Lg Electronics Inc. Turbo fan and air conditioner having the same applied thereto
DE202005004180U1 (de) * 2005-03-14 2006-07-27 Ebm-Papst Landshut Gmbh Radialgebläse
US8257034B2 (en) 2005-03-14 2012-09-04 ERM-Papst Landshut GmbH Radial fan
CN106884804A (zh) * 2015-12-16 2017-06-23 株式会社电装 离心式鼓风机

Also Published As

Publication number Publication date
DE4009869A1 (de) 1991-10-02
EP0450272B1 (fr) 1994-09-21
DE59102983D1 (de) 1994-10-27
EP0450272A3 (en) 1991-12-04

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