WO2011051002A1 - Ventilateur radial - Google Patents

Ventilateur radial Download PDF

Info

Publication number
WO2011051002A1
WO2011051002A1 PCT/EP2010/060998 EP2010060998W WO2011051002A1 WO 2011051002 A1 WO2011051002 A1 WO 2011051002A1 EP 2010060998 W EP2010060998 W EP 2010060998W WO 2011051002 A1 WO2011051002 A1 WO 2011051002A1
Authority
WO
WIPO (PCT)
Prior art keywords
flow
housing
diffuser
cross
flow section
Prior art date
Application number
PCT/EP2010/060998
Other languages
German (de)
English (en)
Inventor
Roland Keber
Tobias Metz
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
Priority to EP10739586.5A priority Critical patent/EP2494212B1/fr
Publication of WO2011051002A1 publication Critical patent/WO2011051002A1/fr

Links

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
    • F04D29/422—Discharge tongues
    • 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
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/44—Fluid-guiding means, e.g. diffusers
    • F04D29/441—Fluid-guiding means, e.g. diffusers especially adapted for elastic fluid pumps
    • 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
    • F05D2250/00—Geometry
    • F05D2250/50—Inlet or outlet
    • F05D2250/52—Outlet

Definitions

  • the invention relates to a radial blower with a housing and an impeller arranged therein, around which a pressure space substantially spiraling in the flow direction is formed, wherein in the housing a tongue is arranged, which extends with its free end substantially in the circumferential direction and a diffuser is formed on the housing, which has a plurality of flow sections, wherein at least a first of the flow sections extends within the housing and wherein the cross sections of the flow sections increase at least in sections towards the air outlet.
  • the fan assemblies of the present invention are often used in the heating industry as premixing blowers, usually gas and air being premixed into an ignitable mixture.
  • a tongue causes the flow to "peel off."
  • a tongue is disclosed, for example, in European application number 04 400 016.4 Rather, the tongue is not simply parallel to the axis of rotation, but rises from the spiral at acute angles, and the structure of the tongue also significantly affects the noise of the fan.
  • the diffuser is usually placed after completion of the spiral shape of the housing to provide for maximum pressure recovery.
  • this is accompanied by an enlarged installation space of the radial fan.
  • the initial cross section of the diffuser is not clearly determinable. Due to this vagueness of the diffuser is often designed too small or too large, so that not the maximum possible pressure is recovered or breaks off the flow in the diffuser. If the tongue is not formed as an extra component, as described above, but formed as a simple step, there is a risk of flow separation especially in the region following the tongue in the direction of flow.
  • the diffusers arranged in the region of the air outlet should not have a larger opening angle than 10 ° in any direction in order to reliably prevent separation of the flow.
  • the maximum pressure recovery in a diffuser at given Spiralendquerites is determined. If the dimensions of the diffuser are limited by structural or manufacturing reasons in individual directions, an optimal design of the diffuser is not possible.
  • a diffuser is formed such that no flow separation occurs, even if individual opening angles are greater than 10 °. This is achieved in particular by the fact that the diffuser is not connected downstream of the spiral-shaped housing, but is already at least partially formed in the interior of the spiral housing, as a result of which both an essentially loss-free flow and a low construction volume are achieved.
  • the diffuser has a plurality of flow sections, preferably three of them, wherein the first flow section is still within the housing, the second flow section is in the region following the free end of the tongue in the flow direction, and the third flow section is in the upstream region of the air flow. or mixture outlet extends.
  • the fan housing is formed substantially round in addition to the spiral extension, so that, starting from the axis of the impeller, different Determine the angle of the outer peripheral housing.
  • the angle ⁇ the angle is determined over which the tongue extends in the circumferential direction of the fan housing.
  • ß the angle is determined over which extend the tongue and a first flow section of the diffuser in the circumferential direction of the housing.
  • the at least one first flow section of the diffuser extends over an angle ⁇ of at most 50 ° of the outer circumference of the housing within the housing.
  • the second flow section of the diffuser connects to the first flow section in the flow direction and preferably extends over a length between one and two thirds of the total length measured from the end of the first flow section to the air outlet. In this area, it is possible to increase the flow area from the first flow section to the second flow section so that neither flow separation nor excessive noise is exhibited.
  • the diffuser starting from the free end of the tongue to the air outlet, by tuning the overall geometry selectively have an opening angle of about 10 °, without the cited by the literature flow separation occurs.
  • this is achieved in that a first replacement angle of one at the end of the first flow Section formed cross-sectional area to a cross-sectional area formed at the end of the second flow section is less than 10 °.
  • a second replacement angle of a cross-sectional area formed at the end of the second flow section to a cross-sectional area formed at the air outlet is preferably less than 7 °.
  • the replacement angle is formed for the blower according to the invention by the following formula, A1 defining the cross-sectional area at the end of the first flow section, A2 the cross-sectional area at the end of the second flow section, D the hydraulic diameter at the end of the first flow section, and d the length of the second flow section:
  • the diffuser in the region of the third flow section which follows the second flow section in the flow direction, may be formed as a manifold in order to minimize the required installation space.
  • the material and space required for an additional manifold is very high, because in addition to the blower housing and the diffuser an additional component is placed, which itself must be equipped with large radii in order to exclude flow separation. It is also difficult to match extra components precisely to minimize the disadvantages mentioned.
  • the manifold in the diffuser, wherein the manifold is preferably formed such that the normal of the cross section at the end of the second flow section to the normal of the cross section at the air outlet at an angle of at least 15 °, but at most 80 °. In between, any angles are possible.
  • the cross-section of the diffuser or the bend in the region of the air outlet is formed substantially with an aspect ratio of 4: 3, wherein the housing wall extending from the tongue to the air outlet is curved in the direction of the center the cross-sectional area at the air outlet ends. The flow can thus be performed in the tongue following area, without detaching, to the air outlet at the manifold.
  • the housing can be formed from a lower part and a cover, wherein the cover in the third flow section (elbow) has a ramp extending in the direction of the lower part.
  • “Ramp” is understood to mean any form of training that extends from the cover in the direction of the lower part in such a way that the cross-section is reduced.
  • the ramp can extend over the entire width or can be provided only in sections. when the end of the ramp in the area of the air outlet with the
  • the height of the diffuser in the second flow section increases substantially steadily and decreases substantially steadily in the region of the third flow section.
  • the height reduction may be possible in an embodiment by the provision of the ramp. As the height direction while the axial direction of the impeller is defined.
  • a diffuser can be provided on a radial fan that is constructed so that no flow separation occurs, even if individual areas of the diffuser or manifold have an opening angle greater than 10 °. Due to the specific design of the replacement angle in the various flow sections and by the initiation of the diffuser effect in the interior of the spiral housing and the formation of the third flow section as a manifold a small volume of construction with maximum efficiency and extremely low noise is achieved. Further features, advantages and embodiments of the invention are the subject of the following description and the schematic representation of an embodiment. Show it
  • FIG. 1 is a plan view of a radial fan with integrated diffuser
  • Fig. 2 is a side sectional view of the radial fan of FIG. 1st
  • the housing 1 shows a radial blower 1 with a housing 2 and an impeller 3 arranged therein.
  • the housing 2 has a substantially spiral shape, wherein in the outside area in the flow direction a pressure chamber 4 which widens substantially continuously in the circumferential direction is formed, which in the end area in FIG a formed on the housing diffuser 6 passes.
  • the diffuser 6 has three flow sections X, Y, Z, wherein the first flow section X within the housing 2 and the third flow section Z are formed as a manifold 8.
  • the flow cross sections of the diffuser 6 enlarge at least in sections in all sections X, Y, Z, wherein in the first and second flow section X, Y there is a substantially continuous enlargement.
  • the tongue 5 In the region of the end of the spiral of the housing 2 there is provided a circumferentially arranged tongue 5 whose free end 5 'forms the beginning of the spiral shape and which serves for "peeling" and subsequent application of the flow In the circumferential direction, the tongue 5 extends through the angle a, in the present case by about 30 °, measured from the free end 5 'of the tongue to one to the end of the second flow section
  • the first flow section X of the diffuser 6 formed in the interior of the housing surrounds the circumference of the housing by the angle ⁇ , which occupies approximately 70 ° as shown in Fig. 2.
  • the diffuser 6 opens by more than 10 °, the replacement angle of the respective arranged at the end of the flow sections cross-sectional areas A1, A2, C meet the criterion that the replacement angle of A1 to A2 is less than 10 ° and from A2 to C is less than 7 °.
  • the replacement angle is here according to the formula where D is the hydraulic diameter at the flow inlet at the cross-sectional area A1 and d is the distance between the cross-sectional areas A1 and A2. In any case, d is to be chosen such that the third flow section Z extends at the second flow section Y for a length of one to two thirds of the total length from the cross-sectional area A1 to the exit surface C.
  • the tongue 5 extends from its free end 5 'tangentially to the housing wall substantially in the direction of the main axis of the diffuser 6 and then passes in the third flow section Z in a substantially parallel to the outer wall of the diffuser shape (seen in plan view).
  • the diffuser 6 is designed so that the end cross-section does not change more than a certain amount, starting from the starting cross-section, in order to prevent separation of the flow.
  • the third flow section Z formed as a manifold 8 at the air outlet has a substantially rectangular shape with an aspect ratio of 4: 3, wherein the housing wall extending from the tongue 5 to the air outlet 7 ends arcuately to the center of the cross-sectional area C at the air outlet 7.
  • FIG. 2 is a sectional view of the radial fan of Fig. 1 is shown.
  • the housing 2 has a lower part 2 'and a lid 2 "which are fastened to one another
  • the fan wheel 3 arranged in the interior of the housing 2 extends in a radial direction into the first and second flow sections X, Y of the diffuser 6.
  • the Dif - Fusor 6 increases steadily in height direction h in the first and second flow section Y, Y, wherein the height h in sections in the third flow section Z by a arranged in the region of the air outlet ramp 9 on the cover 2 "is reduced.
  • the ramp 9 is flush with the lower housing part 2 'in the region of the air outlet 7 and ensures permanent contact of the flow over the entire length of the diffuser in the vertical direction.
  • the formed as a manifold 8 third flow section Z directs the flow by an angle ⁇ of about 60 °, which is formed by the normal of the cross section A2 to the normal of the cross section C.
  • ⁇ of about 60 °
  • the invention is not limited in its execution to the embodiment shown above. Rather, a number of variants are conceivable, which make use of the illustrated solution even with fundamentally different embodiments and are also within the scope of the invention.

Landscapes

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

Abstract

L'invention concerne un ventilateur radial (1) comprenant un boîtier (2) et, logé dans ce dernier, une roue de ventilateur (3) autour de laquelle se forme une chambre de pression (4) qui s'agrandit sensiblement en forme de spirale dans le sens d'écoulement. Une langue (5) s'étend par son extrémité libre (5) sensiblement dans la direction périphérique du boîtier (2). Le boîtier (2) présente un diffuseur (6) comportant plusieurs sections d'écoulement (X, Y, Z), au moins une première section d'écoulement (X) s'étendant dans le boîtier (2) et la coupe transversale des sections d'écoulement (X, Y, Z) allant croissante, au moins par sections, en direction de la sortie d'air (7).
PCT/EP2010/060998 2009-10-26 2010-07-29 Ventilateur radial WO2011051002A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP10739586.5A EP2494212B1 (fr) 2009-10-26 2010-07-29 Ventilateur radial

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102009050684.5 2009-10-26
DE102009050684A DE102009050684A1 (de) 2009-10-26 2009-10-26 Radialgebläse

Publications (1)

Publication Number Publication Date
WO2011051002A1 true WO2011051002A1 (fr) 2011-05-05

Family

ID=42808929

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2010/060998 WO2011051002A1 (fr) 2009-10-26 2010-07-29 Ventilateur radial

Country Status (4)

Country Link
EP (1) EP2494212B1 (fr)
DE (1) DE102009050684A1 (fr)
NL (1) NL1038334C2 (fr)
WO (1) WO2011051002A1 (fr)

Cited By (21)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8839815B2 (en) 2011-12-15 2014-09-23 Honeywell International Inc. Gas valve with electronic cycle counter
US8899264B2 (en) 2011-12-15 2014-12-02 Honeywell International Inc. Gas valve with electronic proof of closure system
US8905063B2 (en) 2011-12-15 2014-12-09 Honeywell International Inc. Gas valve with fuel rate monitor
US8947242B2 (en) 2011-12-15 2015-02-03 Honeywell International Inc. Gas valve with valve leakage test
US9074770B2 (en) 2011-12-15 2015-07-07 Honeywell International Inc. Gas valve with electronic valve proving system
US9234661B2 (en) 2012-09-15 2016-01-12 Honeywell International Inc. Burner control system
US9557059B2 (en) 2011-12-15 2017-01-31 Honeywell International Inc Gas valve with communication link
US9645584B2 (en) 2014-09-17 2017-05-09 Honeywell International Inc. Gas valve with electronic health monitoring
US9683674B2 (en) 2013-10-29 2017-06-20 Honeywell Technologies Sarl Regulating device
US9835265B2 (en) 2011-12-15 2017-12-05 Honeywell International Inc. Valve with actuator diagnostics
US9841122B2 (en) 2014-09-09 2017-12-12 Honeywell International Inc. Gas valve with electronic valve proving system
US9846440B2 (en) 2011-12-15 2017-12-19 Honeywell International Inc. Valve controller configured to estimate fuel comsumption
US9851103B2 (en) 2011-12-15 2017-12-26 Honeywell International Inc. Gas valve with overpressure diagnostics
US9995486B2 (en) 2011-12-15 2018-06-12 Honeywell International Inc. Gas valve with high/low gas pressure detection
US10024439B2 (en) 2013-12-16 2018-07-17 Honeywell International Inc. Valve over-travel mechanism
US10422531B2 (en) 2012-09-15 2019-09-24 Honeywell International Inc. System and approach for controlling a combustion chamber
US10503181B2 (en) 2016-01-13 2019-12-10 Honeywell International Inc. Pressure regulator
US10564062B2 (en) 2016-10-19 2020-02-18 Honeywell International Inc. Human-machine interface for gas valve
US10697815B2 (en) 2018-06-09 2020-06-30 Honeywell International Inc. System and methods for mitigating condensation in a sensor module
US11073281B2 (en) 2017-12-29 2021-07-27 Honeywell International Inc. Closed-loop programming and control of a combustion appliance
DE102021128167A1 (de) 2021-10-28 2023-05-04 Alfred Kärcher SE & Co. KG Reinigungsvorrichtung und Verwendung eines Strömungsumlenkungselements

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
BE1022028B1 (nl) 2013-04-05 2016-02-04 Atlas Copco Airpower, Naamloze Vennootschap Behuizing voor een ventilator van een spiraalcompressor
DE202015104586U1 (de) 2015-08-28 2015-09-15 Ebm-Papst Mulfingen Gmbh & Co. Kg Spiralgehäuse eines Radialventilators
DE102015114389A1 (de) 2015-08-28 2017-03-02 Ebm-Papst Mulfingen Gmbh & Co. Kg Spiralgehäuse eines Radialventilators

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1984003740A1 (fr) * 1983-03-19 1984-09-27 Vaillant Joh Gmbh & Co Soufflante radiale
US6314894B1 (en) * 2000-08-30 2001-11-13 Jakel Incorporated Furnace blower housing with integrally formed exhaust transition
US20030049122A1 (en) * 2001-08-28 2003-03-13 Kim Sung Chun Blower
US20040062646A1 (en) * 2002-06-26 2004-04-01 Tadahiro Nomura Centrifugal air blower
EP2006610A1 (fr) * 2007-05-31 2008-12-24 CO.ME.FRI. S.p.A. Unité pour le traitement d'air avec un débit contrôlé

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1984003740A1 (fr) * 1983-03-19 1984-09-27 Vaillant Joh Gmbh & Co Soufflante radiale
US6314894B1 (en) * 2000-08-30 2001-11-13 Jakel Incorporated Furnace blower housing with integrally formed exhaust transition
US20030049122A1 (en) * 2001-08-28 2003-03-13 Kim Sung Chun Blower
US20040062646A1 (en) * 2002-06-26 2004-04-01 Tadahiro Nomura Centrifugal air blower
EP2006610A1 (fr) * 2007-05-31 2008-12-24 CO.ME.FRI. S.p.A. Unité pour le traitement d'air avec un débit contrôlé

Cited By (28)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9846440B2 (en) 2011-12-15 2017-12-19 Honeywell International Inc. Valve controller configured to estimate fuel comsumption
US8899264B2 (en) 2011-12-15 2014-12-02 Honeywell International Inc. Gas valve with electronic proof of closure system
US8905063B2 (en) 2011-12-15 2014-12-09 Honeywell International Inc. Gas valve with fuel rate monitor
US8947242B2 (en) 2011-12-15 2015-02-03 Honeywell International Inc. Gas valve with valve leakage test
US9074770B2 (en) 2011-12-15 2015-07-07 Honeywell International Inc. Gas valve with electronic valve proving system
US10697632B2 (en) 2011-12-15 2020-06-30 Honeywell International Inc. Gas valve with communication link
US9557059B2 (en) 2011-12-15 2017-01-31 Honeywell International Inc Gas valve with communication link
US8839815B2 (en) 2011-12-15 2014-09-23 Honeywell International Inc. Gas valve with electronic cycle counter
US10851993B2 (en) 2011-12-15 2020-12-01 Honeywell International Inc. Gas valve with overpressure diagnostics
US9995486B2 (en) 2011-12-15 2018-06-12 Honeywell International Inc. Gas valve with high/low gas pressure detection
US9835265B2 (en) 2011-12-15 2017-12-05 Honeywell International Inc. Valve with actuator diagnostics
US9851103B2 (en) 2011-12-15 2017-12-26 Honeywell International Inc. Gas valve with overpressure diagnostics
US9234661B2 (en) 2012-09-15 2016-01-12 Honeywell International Inc. Burner control system
US11421875B2 (en) 2012-09-15 2022-08-23 Honeywell International Inc. Burner control system
US10422531B2 (en) 2012-09-15 2019-09-24 Honeywell International Inc. System and approach for controlling a combustion chamber
US9657946B2 (en) 2012-09-15 2017-05-23 Honeywell International Inc. Burner control system
US9683674B2 (en) 2013-10-29 2017-06-20 Honeywell Technologies Sarl Regulating device
US10215291B2 (en) 2013-10-29 2019-02-26 Honeywell International Inc. Regulating device
US10024439B2 (en) 2013-12-16 2018-07-17 Honeywell International Inc. Valve over-travel mechanism
US9841122B2 (en) 2014-09-09 2017-12-12 Honeywell International Inc. Gas valve with electronic valve proving system
US9645584B2 (en) 2014-09-17 2017-05-09 Honeywell International Inc. Gas valve with electronic health monitoring
US10203049B2 (en) 2014-09-17 2019-02-12 Honeywell International Inc. Gas valve with electronic health monitoring
US10503181B2 (en) 2016-01-13 2019-12-10 Honeywell International Inc. Pressure regulator
US10564062B2 (en) 2016-10-19 2020-02-18 Honeywell International Inc. Human-machine interface for gas valve
US11073281B2 (en) 2017-12-29 2021-07-27 Honeywell International Inc. Closed-loop programming and control of a combustion appliance
US10697815B2 (en) 2018-06-09 2020-06-30 Honeywell International Inc. System and methods for mitigating condensation in a sensor module
DE102021128167A1 (de) 2021-10-28 2023-05-04 Alfred Kärcher SE & Co. KG Reinigungsvorrichtung und Verwendung eines Strömungsumlenkungselements
WO2023073009A1 (fr) 2021-10-28 2023-05-04 Alfred Kärcher SE & Co. KG Dispositif de nettoyage et utilisation d'un élément de déviation d'écoulement

Also Published As

Publication number Publication date
EP2494212A1 (fr) 2012-09-05
DE102009050684A1 (de) 2011-04-28
EP2494212B1 (fr) 2016-11-16
NL1038334C2 (nl) 2012-03-27
NL1038334A (nl) 2011-04-27

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