EP2196679A2 - Roue pour un ventilateur radiale - Google Patents

Roue pour un ventilateur radiale Download PDF

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Publication number
EP2196679A2
EP2196679A2 EP10157619A EP10157619A EP2196679A2 EP 2196679 A2 EP2196679 A2 EP 2196679A2 EP 10157619 A EP10157619 A EP 10157619A EP 10157619 A EP10157619 A EP 10157619A EP 2196679 A2 EP2196679 A2 EP 2196679A2
Authority
EP
European Patent Office
Prior art keywords
radial fan
fan wheel
wheel according
blades
radial
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
EP10157619A
Other languages
German (de)
English (en)
Other versions
EP2196679A3 (fr
EP2196679B1 (fr
Inventor
Roland Keber
Rudolf Tungl
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 Landshut GmbH
Original Assignee
Ebm Papst Landshut 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 Ebm Papst Landshut GmbH filed Critical Ebm Papst Landshut GmbH
Publication of EP2196679A2 publication Critical patent/EP2196679A2/fr
Publication of EP2196679A3 publication Critical patent/EP2196679A3/fr
Application granted granted Critical
Publication of EP2196679B1 publication Critical patent/EP2196679B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F04D29/26—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
    • 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
    • F04D29/02—Selection of particular materials
    • F04D29/023—Selection of particular materials especially adapted for elastic fluid pumps
    • 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
    • F04D29/284—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for compressors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2230/00—Manufacture
    • F05D2230/50—Building or constructing in particular ways
    • F05D2230/53—Building or constructing in particular ways by integrally manufacturing a component, e.g. by milling from a billet or one piece construction
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2300/00—Materials; Properties thereof
    • F05D2300/40—Organic materials
    • F05D2300/43—Synthetic polymers, e.g. plastics; Rubber

Definitions

  • the present invention relates to a radial impeller, in particular for use in gas blowers with a steep fan characteristic curve.
  • the EP 0 410 271 B1 describes a radial fan for conveying a gaseous medium in a device with high flow resistance, which is in particular a burner in a gas boiler. Such burners have a relatively high flow resistance, which is of the order of 200 Pascal or more.
  • the medium to be conveyed may be air or a combustible gas-air mixture.
  • the blower or its blower wheel must therefore be designed for a steep pressure-volume flow characteristic. This means that pressure changes should be accompanied by only small changes in the volume flow.
  • the known fan has for this purpose an impeller whose diameter is more than ten times its flow outlet width.
  • This is a closed, both sides capped wheel with a substantially flat and a central hub having lower part (first cover plate), a plurality of backwardly curved, each having the shape of a circular section blades and a circular, flat-plate-shaped lid (second cover plate ) with a central, circular inlet opening.
  • the present invention has for its object to provide a Radialgebläserad, which is particularly suitable for a gas burner fan with steep curve in a simple and economical manner to produce.
  • the diameter As at least ten times the flow outlet width of the blades, the desired steep characteristic is achieved.
  • the blades have on their side facing away from the cover plate side free edges, which lie in an imaginary plane or any curved surface.
  • the radial impeller according to the invention is intended for use in a blower housing which has a wall adapted to the free blade side edges or to the imaginary surface shape defined by these, such that only a narrow axial gap is formed between this wall and the impeller blades is.
  • the invention provided in each case between two blades shortened intermediate blades have the advantage that on the one hand a relatively large number of blades or vanes can be provided, which is advantageous in terms of flow guidance in the flow channels formed between the blades with regard to air flow, flow separation and vortex formation.
  • the problem is avoided that with a correspondingly large number of long blades passing through to the inlet region, the intake or inflow region would be partially blocked, which would have a negative effect on the delivery volume.
  • the radially inner inflow region is kept open in the region of the shorter intermediate vanes.
  • annular cover plate which has a width R D , which is measured from the edge of the suction port is smaller than the distance Rand- suction to discharge opening - peripheral edge.
  • width is such that it is measured from the intake substantially half a blade length.
  • This particular embodiment also allows a production of the impeller as a one-piece molded part, being considered as particularly favorable an embodiment in which the support disc is annular and has a ring width, which is substantially the dimension outer edge cover plate to exit opening-Umfangsrand (2-3 '. ) is.
  • this ring width is substantially half a blade length, guidance may still be given to the airflow in the exit region, so that the shear friction between the rearward housing wall and the flow is restricted to a reduced range.
  • the two disc rings namely that of the cover disc and that of the support disc, either overlap in the projection in the direction of the axis of rotation as required, form a gap between them or themselves then add each other to a circular area.
  • An advantageous flow course can be achieved in that the hub body has a height that corresponds to measured from the plane of the rear support plate substantially half the wheel depth.
  • a cone is formed on the hub body to the flow side, wherein the cover plate (2-9) and the cone of the hub in cross section AA have substantially a parallel course. As a result, a favorable flow profile is achieved in the input region of the wheel.
  • the flow surface is substantially parallel to the plane of rotation.
  • the flow surface of the outer peripheral portion is arranged in a plane which is located with respect to the flow channel inwardly than the surface of the outer support disc bounding the flow channel, d. That is, the support disk can be made thinner than the thickness of the outer peripheral portion of the cone.
  • An advantageous embodiment can be designed so that the blades are axially wider in the intake area than in the outflow area.
  • At least one intermediate blade is arranged between the blades substantially in the region of the width of the carrier disk.
  • each case two intermediate blades are arranged in pairs. It is particularly advantageous if the intermediate blades have a radial extent which corresponds substantially to the distance between the outer periphery of the cover plate and the outer periphery of the rear support plate.
  • the intermediate blades are held exclusively on the rear support plate.
  • This embodiment particularly facilitates the formation of the radial impeller as a one-piece cast part.
  • An inventive radial impeller 1 consists of a plurality of distributed over the circumference arranged radial blades 2, seen in the radial direction extend from an inner inlet region 4 to an outer exit region 6.
  • the blades 2 have radially inner end edges 8, which are located on an imaginary, approximately cylindrical, but especially conical surrounding the inlet region 4 and in the axial inflow direction (see the arrow E in FIG Fig. 1 and 4 to 6 ) seen in the inlet region 4 in the tapered surface lie.
  • the blades 2 also have outer end edges 10.
  • radial flow channels 12 are formed with a substantially radial outflow direction A.
  • the blades 2 extend axially, ie viewed in the direction of a rotation axis 14, between an inlet side 16 and an axially opposite hub side 18 (see the sectional views in FIG 4 to 6 ).
  • the blades 2 are furthermore connected according to the invention only on their inlet side 16 over their radial extent to the outlet region 6 with a cover plate 20 which has a central inlet opening 22 opening into the inlet region 4.
  • the blades are connected only with their radially inner end regions with a central hub 24, so that the flow channels 12 are formed open on this side in the axial direction.
  • the blades 2 thus have free side edges 26 on this side.
  • the blades 2 and the cover plate 20 has an outer impeller diameter D, which is at least ten times an existing in the exit region 6, axially measured flow outlet width B of the blades.
  • the axially measured inner flow inlet width C of the blades 2 in the inlet region 4 is preferably greater than the outer flow outlet width in the outlet region 6 (cf., for example, FIG Fig. 4 ).
  • radially shorter intermediate blades 28 are connected to the cover disk 20 in regions respectively arranged between adjacent blades 2 (see in particular FIG Fig. 1 and 2 ). These intermediate blades 28 extend from the outer circumference of the cover plate 20 only over part of the radial extent of the cover plate 20 and terminate at a radial distance from the hub 24. This can best be seen in Fig. 2 detect. In the illustrated embodiment, only one intermediate blade 28 is provided between each two adjacent blades 2, but it can also each two or more intermediate blades Be provided 28, which can then be designed with the same or different radial length.
  • the radial impeller 1 can be advantageously prepared as a one-piece molded plastic, preferably of a plastic with such antistatic properties that during operation static charges avoided or derived via a not shown housing. This contributes to a high degree of application safety, especially with regard to the preferred application for conveying combustible gas-air mixtures, by avoiding ignition by sparking.
  • the blades 2 and the intermediate blades 28 are formed in the radial direction with respect to the direction of rotation 30 is curved backward.
  • the blades are arranged such that their entry angle is approximately between 30 ° and 45 ° and their exit angle is approximately between 45 ° and 90 °. To explain this angle is on the EP 0 410 271 Referenced.
  • an embodiment with forward curved or at the exit region 6 radially ending blades 2 and intermediate blades 28 is possible.
  • the hub 24 consists of an outer disk portion 32 and a central, to be connected to a shaft not shown bearing portion 34, in particular in the form of a short pipe socket.
  • the disc portion 32 is connected at its radially outer periphery with the inner, the inlet portion 4 facing end portions of the blades.
  • the disc portion 32 of the hub 24 is projecting from its outer peripheral region connected to the blades 2 such in the inlet region 4 and in the direction of the inflow opening 22 of the cover plate 20 projecting convexly or cup-shaped, for example, that the hub 24 -. see in particular Fig.
  • blower-functional elements such as bearing elements, motor or rotor parts and / or the like.
  • the blades 2 and the intermediate blades 28 are connected in their radially outer and the cover plate 20 axially opposite region for mechanical reinforcement via a circumferential, integrally molded ring member 40.
  • the cover disk 20 in the region of the inflow opening 22 has a nozzle-like edge 42 in the flow direction.
  • Fig. 7 and 8th is shown a further embodiment for solving the problem of the invention.
  • the reference numerals of the preceding embodiments are provided with a number 2 and hyphen in the embodiment described now.
  • radial impeller 2-1 has an annular cover plate 2-9, which surrounds the suction 2-7 annular. Usually, a circular suction opening 2-10 is formed on the cover plate 2-9, which is surrounded by a circumferential opening lip 2-10 '.
  • the radial impeller 2-1 further includes a hub body 2-2 and a peripheral edge 2-3.
  • the hub body 2-2 has on its side facing the suction opening 2-10 a cone 2-2 'on.
  • the impeller 2-1 is equipped with the hub body 2-2 to the peripheral edge 2-3 substantially radially extending blades 2-6.
  • the vanes define an intake region 2-7 and an outflow region 2-8.
  • the annular cover plate 2-9 has a width R D , which measured from the edge of the suction port (2-10) is half the distance edge-outlet opening circumference 2-3.
  • the width R D thus corresponds to substantially half of the blade length measured along the upper peripheral edge of the blade 2-6.
  • the foot of such a blade is integrally connected at its radially inner tip with the hub body.
  • the support disk 2-11 extending on the rear side 2-5 is ring-shaped and has a width R T on its ring, which measured from the edge of the suction port 2-10, substantially half of the design edge outlet opening 2-10- peripheral edge is 2-3. This corresponds essentially to half the length of the blade, measured along the back edge of the blade jet between the peripheral edge 2-3 and the base of the blade 2-6 on the cone 2-2 'of the hub 2-2.
  • the hub body 2-2 has a height which, measured from the plane of the rear support plate 2-11 substantially equal to half the wheel height. In the illustrated embodiment, the height of the hub corresponds to half the height of the projecting into the suction port 2-10 blades.
  • the surface F K of the cone 2-2 'of the hub 2-2 extends substantially parallel to the inner surface F D cover plate 2-9.
  • a region 2-21 is formed, the surface of which runs essentially parallel to the plane of rotation of the impeller.
  • the flow-facing surface of the cone and the rotation-parallel region are rounded.
  • intermediate blades 2-16 are arranged substantially in the region of the width of the rear support disk 2-11.
  • the number of blades 2-16 may vary depending on the application.
  • two intermediate blades 2-16 are arranged in pairs between two blades 2-6.
  • the radial extent of the intermediate blades 2-16 is dimensioned so that it substantially corresponds to the distance 2-17 between the outer periphery 2-18 of the cover plate 2-9 and the outer periphery 2-19 of the rear support plate 2-11.
  • the intermediate blades 2-16 are held exclusively on the rear support plate 2-11, that is, the front edge of the intermediate blades are free in this embodiment.
  • the intermediate blades can also be formed on the cover plate.
  • the Shape of the intermediate blades corresponds in its course substantially the corresponding design of the portion of the blades 2-6 at the appropriate location.
  • the preceding embodiment can also advantageously be produced as a one-piece molded part made of plastic

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
EP10157619.7A 2004-07-31 2005-07-29 Roue pour un ventilateur radiale Active EP2196679B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE202004012015U DE202004012015U1 (de) 2004-07-31 2004-07-31 Radialgebläserad
EP05768016A EP1774180B1 (fr) 2004-07-31 2005-07-29 Roue de soufflante radiale

Related Parent Applications (2)

Application Number Title Priority Date Filing Date
EP05768016A Division EP1774180B1 (fr) 2004-07-31 2005-07-29 Roue de soufflante radiale
EP05768016.7 Division 2005-07-29

Publications (3)

Publication Number Publication Date
EP2196679A2 true EP2196679A2 (fr) 2010-06-16
EP2196679A3 EP2196679A3 (fr) 2013-12-18
EP2196679B1 EP2196679B1 (fr) 2015-11-25

Family

ID=35453467

Family Applications (2)

Application Number Title Priority Date Filing Date
EP10157619.7A Active EP2196679B1 (fr) 2004-07-31 2005-07-29 Roue pour un ventilateur radiale
EP05768016A Active EP1774180B1 (fr) 2004-07-31 2005-07-29 Roue de soufflante radiale

Family Applications After (1)

Application Number Title Priority Date Filing Date
EP05768016A Active EP1774180B1 (fr) 2004-07-31 2005-07-29 Roue de soufflante radiale

Country Status (5)

Country Link
US (2) US7794206B2 (fr)
EP (2) EP2196679B1 (fr)
AT (1) ATE544953T1 (fr)
DE (1) DE202004012015U1 (fr)
WO (1) WO2006013067A2 (fr)

Cited By (1)

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Publication number Priority date Publication date Assignee Title
EP3530956A1 (fr) 2018-02-26 2019-08-28 Honeywell Technologies Sarl Roue à aubes pour soufflante radiale et appareil à brûleur à gaz

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EP3530956A1 (fr) 2018-02-26 2019-08-28 Honeywell Technologies Sarl Roue à aubes pour soufflante radiale et appareil à brûleur à gaz
US11067095B2 (en) 2018-02-26 2021-07-20 Honeywell Technologies Sarl Impeller for a radial fan and gas burner appliance

Also Published As

Publication number Publication date
EP2196679A3 (fr) 2013-12-18
EP1774180B1 (fr) 2012-02-08
US20100098544A1 (en) 2010-04-22
ATE544953T1 (de) 2012-02-15
EP2196679B1 (fr) 2015-11-25
WO2006013067A3 (fr) 2006-12-28
WO2006013067A2 (fr) 2006-02-09
US8109731B2 (en) 2012-02-07
US20080292464A1 (en) 2008-11-27
DE202004012015U1 (de) 2005-12-22
US7794206B2 (en) 2010-09-14
EP1774180A2 (fr) 2007-04-18

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