EP1616101B2 - Lüfter - Google Patents

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Publication number
EP1616101B2
EP1616101B2 EP04727247.1A EP04727247A EP1616101B2 EP 1616101 B2 EP1616101 B2 EP 1616101B2 EP 04727247 A EP04727247 A EP 04727247A EP 1616101 B2 EP1616101 B2 EP 1616101B2
Authority
EP
European Patent Office
Prior art keywords
fan
blades
region
edge
blade
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
EP04727247.1A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP1616101A1 (de
EP1616101B1 (de
Inventor
Georg Eimer
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Ebm Papst St Georgen GmbH and Co KG
Original Assignee
Ebm Papst St Georgen GmbH and Co KG
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Filing date
Publication date
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Application filed by Ebm Papst St Georgen GmbH and Co KG filed Critical Ebm Papst St Georgen GmbH and Co KG
Publication of EP1616101A1 publication Critical patent/EP1616101A1/de
Publication of EP1616101B1 publication Critical patent/EP1616101B1/de
Application granted granted Critical
Publication of EP1616101B2 publication Critical patent/EP1616101B2/de
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
    • F04D29/08—Sealings
    • F04D29/16—Sealings between pressure and suction sides
    • F04D29/161—Sealings between pressure and suction sides especially adapted for elastic fluid pumps
    • F04D29/164—Sealings between pressure and suction sides especially adapted for elastic fluid pumps of an axial flow wheel
    • 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
    • F04D29/32—Rotors specially for elastic fluids for axial flow pumps
    • F04D29/38—Blades
    • F04D29/384—Blades characterised by form
    • 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
    • F05D2240/00—Components
    • F05D2240/20—Rotors
    • F05D2240/30—Characteristics of rotor blades, i.e. of any element transforming dynamic fluid energy to or from rotational energy and being attached to a rotor
    • F05D2240/307—Characteristics of rotor blades, i.e. of any element transforming dynamic fluid energy to or from rotational energy and being attached to a rotor related to the tip of a rotor blade

Definitions

  • the invention relates to a device fan with an air conveyor channel and a rotatably mounted therein fan, the wings are provided in the region of its outer edges with flow elements that are resistant to resistance to the flow and for the around the outer edges of the wings from the pressure to the suction side extending balance flows constitute an obstacle.
  • a device fan with such flow elements is known from the DE-A-3017226 , This shows various constructions of such flow elements in connection with stamped fan blades made of sheet metal. These flow elements reduce the leakage flow in a fan equipped with it.
  • a device fan with an outer casing, the inside of which is penetrated by an air conveying channel in which a fan wheel is arranged, which is rotatable about a central axis and has a central hub with an outer circumference on which fan blades are fixed, their radial outer edges each a distance from the adjacent inside of the fan housing.
  • These wings have a profile which is formed similar to the airfoil profile of an aircraft, wherein the wings are concave and sickle-shaped at the front edge, have a convex trailing edge, and are wound.
  • a blade shroud is placed around the blades and this forms with the fan housing a channel for air flowing back from the pressure side of the fan to its suction side.
  • This back-flowing air follows a complicated flow path and is converted on its way through soothing plates in a laminar flow, so that no vortex arise at the intake of the fan. Purpose of the arrangement is a noise reduction at the front edges of the fan blades where they would otherwise meet the vortex of the back flowing air.
  • a flow element is provided which has an analogous course as the associated fan blades, and that for one to this wound radially outer edge of the pressure side to the suction side extending equalizing flow is designed as a flow obstruction to reduce the noise generated during operation of the device fan.
  • Fig. 1 shows a device fan 10 of conventional design.
  • the present invention can be realized with an axial fan and a diagonal fan.
  • the in Fig. 1 shown fan 10 has an outer housing 12, at the four corners of each mounting holes 14 are provided and defines in its interior an air conveyor channel 16 which is bounded outwardly by a rotation surface 17 and in which via webs 18, the central hub 20 of a fan 22nd is rotatably mounted, which in operation of a disposed within this hub 20 electric motor about a central axis 25 (FIG. Fig. 4 and 5 ) is rotated.
  • the hub 20 rotates in the direction of an arrow 24 in the counterclockwise direction. The air flow is so that the air is blown out via the webs 18, ie through the back of the fan 10, based on Fig. 1 ,
  • five fan blades 26, indicated at 26A to 26E, are mounted on the outer periphery 27 of the hub 20.
  • the angular distance beta from the leading edge 28A of the fan blade 26A to the leading edge 28B of the blade 26B is 74 ° in this embodiment.
  • the wings 26 are unevenly distributed around the periphery of the hub to provide a more pleasing frequency spectrum. Naturally, the illustrated type of distribution represents only a preferred embodiment.
  • the leading edges 28A to 28E of the wings 26 are concave and sickle-shaped.
  • the trailing edges of the wings 26 are designated 36A to 36E and convex. They are designed so that their intersection with the webs 18 "schleifend” takes place; So "with a grinding cut”. This means that seen in most or all rotational positions and in plan view, the imaginary intersection between a web 18 and a trailing edge 36 (which of course do not touch), takes place at an angle, such as the Fig. 1 clearly shows. This measure contributes to noise reduction. -
  • the radially outer edges of the wings 26 are designated 40A to 40E. As in Fig. 5 shown, these edges 40 have a radial distance d from the inner side 17 of the outer housing 12. This "air gap" d should be as small as possible. When it is large, flows through it a considerable leakage flow from the pressure side to the suction side of the fan 10th
  • the individual wings 26 are provided in the region of their radially outer edges 40 with flow elements 42A to 42E, namely with widenings of the outer wing edges 40, which preferably extend in the axial direction to the suction side and the pressure side. (In the case of diagonal fans, wings are preferably used in which such flow elements are only on the suction side.)
  • the wings 26 have approximately the cross-sectional shape of an aircraft wing, ie the leading edge 28C is round and relatively blunt. From there, the thickness D of a wing 26 first increases and then decreases again in the direction of the trailing edge 36, and the wing 26 tapers at the trailing edge 36 in order to reduce or avoid the formation of eddies and consequent noise ,
  • the flow elements 42 have a similar course as the associated wing, cf. Fig. 6 that is, they also taper at the trailing edge 36 and are rounded at the leading edge 28, and in the intermediate region 48 between the region of the leading edge 28 and the region of the trailing edge 36 they protrude over the blade 26 by a substantially constant amount in the axial direction - Out, like that FIGS. 5 and 6 clearly show. At both ends, a sliding transition is provided, ie the constant amount there slidingly decreases to zero.
  • the flow elements 42 in conjunction with the narrow air gap d ( Fig. 5 ), provide increased resistance to the leakage flow that, in operation, extends around the outer edge 40 of the vanes 26 from the pressure side to the suction side.
  • the individual wings 26 are wound, ie the point where a wing 26 grows out of the hub 20 so to speak, it has approximately the shape of a threaded portion, and also the outer edges 40 of the wings 26 are formed in the manner of a threaded portion, but as shown, the pitch of the threaded portions in the region of the hub 20 is greater than in the region of radially outer edges 40:
  • Fig. 10 shows for a fan whose wings 26 are not provided with flow elements 42, the pressure increase ⁇ p1 and the sound pressure level Lp1.
  • the curves were measured on a conventional fan test bench, in which on the pressure side of the fan 10, an adjustable throttle (not shown) is arranged.
  • the opening ODR of this throttle is indicated on the horizontal axis with values between 0 and 2500, where "0" means that this throttle is closed.
  • the fan 10 operates in the region of the turbulent flow, with the pressure ⁇ p1 and the sound pressure level Lp1 rising to the left.
  • Figure 11 shows the curves for the described embodiment, ie the fan is indeed the same as in Fig. 10 but the fan 22 is provided with the described flow elements 42.
  • Fig. 13 and 14 show a fan 122 according to a second, particularly preferred embodiment of the invention with a central hub 120.
  • the outer casing of this fan has the same shape as the outer casing 12 of Fig. 1 and is therefore not shown again.
  • the direction of rotation is denoted by 124, ie the fan 122 rotates clockwise.
  • Fig. 14 shows a view of the suction side of the fan wheel 122nd
  • five fan blades 126 are mounted on the outer periphery 127 of the hub 120. These are, as in the first embodiment, unevenly distributed on the periphery 127 of the hub 120 in order to obtain a pleasant frequency spectrum of the fan noise.
  • the leading edges 128A to 128E of the wings 126 are concave and strongly sickle-shaped.
  • the outer end 130A to 130E of the sickles 128, seen in the direction of rotation 124, before the transition point 132A to 132E of the sickles 128 in the hub 120 more preferably, these transition points 132A to 132E, based on the Turning direction 124, lie at the very back, ie the entire sickle 128 extends, as shown, from this transition point 132 in the direction of rotation to the front.
  • an angle ⁇ of approximately 78 ° results, under which the sickle edge 128A emerges from the hub 120.
  • This angle alpha is eg at the Fig. 1 to 12 greater than 90 °. It should preferably be ⁇ 90 ° and has preferred values between 70 and 90 °, in particular between 75 and 85 °.
  • the trailing edges of wings 126A to 126E are designated 136A to 136E and also more arcuately curved than in the version of FIGS Fig. 1 to 12 . Their cut with the webs 18 of the housing 12 also takes place "with schleifendem cut", as in Fig. 1 to 12 described in detail.
  • a shape of the outer housing is used, in which the webs 18 mirror images of Fig. 1 run.
  • the bridge 18 from an outer location, which would correspond to a clock about 6 o'clock, to an inner location, which corresponds to about 8 o'clock.
  • this web 18 from an outer point, which corresponds to about 6 o'clock, to an inner point, which corresponds to about 4 o'clock. This results for the fan wheels of the Fig. 13 and 14 the mentioned "grinding cut".
  • the outer radial edges of the wings 126 are designated 140A to 140E. Analogous Fig. 5 these edges 140 have a small radial distance d from the inside of the fan housing 12. Through the gap formed in this case flows a leakage flow from the pressure side to the suction side of the fan.
  • the individual wings 126 are provided in the region of their radially outer edges 140 with flow elements 142A to 142E, which extend in the axial direction between the suction side and the pressure side.
  • the shape of the flow elements 142 results very well from the illustration according to Fig. 14 which particularly the flow element 142D and a part of the flow element 142C shows very well.
  • the course of the flow elements 142 is the same as in Fig. 6 for the flow element 42C, and the same applies to the profile of the wings 126, so that for this part to the description of the Fig. 1 to 12 can be referenced.
  • the flow elements 142 form an increased resistance to the leakage flow, which in operation extends around the outer edge 140 of the vanes 126 from the pressure side to the suction side.
  • the individual wings 126 are wound, ie the point where a wing 126 grows out of the hub 120 so to speak, has approximately the shape of a threaded portion, and also the outer edges 140 of the wings 126 have approximately the shape of a threaded portion, However, as shown, the thread pitch in the region of the hub 120 is greater than in the region of the radially outer edges 140.
  • Fig. 15 shows in comparison fan characteristics for the impeller 122 without flow elements and the impeller 122 with the flow elements 142, at the same air gap d (as well as in the illustrations of the Fig. 1 to 12 ).
  • the pressure increase for a fan wheel without flow elements 142 is denoted by ⁇ p3
  • the pressure increase for the same fan wheel 122 with the flow elements 142 is denoted by ⁇ p4. It can be seen that without the flow elements 142 a slightly greater pressure increase .DELTA.p results.
  • the sound pressure level for a fan without flow elements is denoted Lp3, and the sound pressure level for the same fan 122 with the elements 142 with Lp4.
  • Lp3 The sound pressure level for a fan without flow elements
  • Lp4 The sound pressure level for the same fan 122 with the elements 142 with Lp4.
  • Fig. 15 With Fig. 12 , it can be seen that due to the stronger sickling of the front edges 128, in conjunction with the flow elements 142, a reduction of the sound pressure level Lp over the entire measuring range results, which is very pronounced especially in the laminar range.
  • the noise reduction depends on in which area of its characteristic curve the fan in question is operated, as is familiar to the fan specialist.
  • One physical reason for the noise reduction could be that an air flow can form in the area of the sacculated leading edges 128 that flows along an entire leading edge 128 from outside to inside and thus to a low circumferential velocity region, the flow elements 142 having a positive influence have the beginning of this air flow.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
EP04727247.1A 2003-04-19 2004-04-14 Lüfter Expired - Lifetime EP1616101B2 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE20306455 2003-04-19
PCT/EP2004/003916 WO2004094835A1 (de) 2003-04-19 2004-04-14 Lüfter

Publications (3)

Publication Number Publication Date
EP1616101A1 EP1616101A1 (de) 2006-01-18
EP1616101B1 EP1616101B1 (de) 2011-03-16
EP1616101B2 true EP1616101B2 (de) 2016-06-15

Family

ID=32520322

Family Applications (1)

Application Number Title Priority Date Filing Date
EP04727247.1A Expired - Lifetime EP1616101B2 (de) 2003-04-19 2004-04-14 Lüfter

Country Status (5)

Country Link
US (1) US7438522B2 (fi)
EP (1) EP1616101B2 (fi)
AT (1) ATE502217T1 (fi)
DE (3) DE102004017727A1 (fi)
WO (1) WO2004094835A1 (fi)

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JP5259919B2 (ja) * 2005-07-21 2013-08-07 ダイキン工業株式会社 軸流ファン
EP1801422B1 (de) * 2005-12-22 2013-06-12 Ziehl-Abegg AG Ventilator und Ventilatorflügel
EP1801421A1 (de) * 2005-12-22 2007-06-27 Ziehl-Abegg AG Ventilator and Ventilatorflügel
US20090263254A1 (en) * 2006-01-05 2009-10-22 Bucher John C Ceiling Fan With High Efficiency Ceiling Fan Blades
US20070154315A1 (en) * 2006-01-05 2007-07-05 Bucher John C Ceiling fan with high efficiency ceiling fan blades
TWI370876B (en) * 2006-01-23 2012-08-21 Delta Electronics Inc Fan and impeller thereof
JP4872722B2 (ja) * 2007-03-12 2012-02-08 ソニー株式会社 軸流ファン装置、軸流羽根車及び電子機器
NL2004352C2 (en) 2010-03-05 2011-09-06 Book Factory Systems B V Small batch book production.
DE102011015784A1 (de) 2010-08-12 2012-02-16 Ziehl-Abegg Ag Ventilator
DE202011004708U1 (de) 2010-08-12 2011-07-14 Ziehl-Abegg Ag Ventilator
DE102010034604A1 (de) 2010-08-13 2012-02-16 Ziehl-Abegg Ag Flügelrad für einen Ventilator
CN102536897B (zh) * 2010-12-29 2015-04-22 台达电子工业股份有限公司 风扇及其叶轮
TWI443262B (zh) * 2010-12-29 2014-07-01 Delta Electronics Inc 風扇及其葉輪
EP2771581B1 (de) * 2011-10-25 2018-12-26 ebm-papst Mulfingen GmbH & Co. KG Axialventilatorrad
DE102012004617A1 (de) * 2012-03-06 2013-09-12 Ziehl-Abegg Ag Axialventilator
US10087764B2 (en) 2012-03-08 2018-10-02 Pratt & Whitney Canada Corp. Airfoil for gas turbine engine
CN102748327A (zh) * 2012-07-31 2012-10-24 洛瓦空气工程(上海)有限公司 带镰刀形前弯叶片的轴流风机叶轮装置
US9404511B2 (en) * 2013-03-13 2016-08-02 Robert Bosch Gmbh Free-tipped axial fan assembly with a thicker blade tip
DE102014102311A1 (de) * 2014-02-21 2015-08-27 Ebm-Papst St. Georgen Gmbh & Co. Kg Lüfter mit einem mit Laufschaufeln versehenen Laufrad
EP3239533A1 (de) 2016-04-29 2017-11-01 STEINBEIS GMBH & CO. Für TECHNOLOGIETRANSFER Axiale turbomaschine
US10527057B2 (en) 2017-09-12 2020-01-07 Delta Electronics, Inc. Fan module
US11142038B2 (en) 2017-12-18 2021-10-12 Carrier Corporation Labyrinth seal for fan assembly
JP6426869B1 (ja) * 2018-06-08 2018-11-21 株式会社グローバルエナジー 横軸ロータ
GB2575297B (en) * 2018-07-05 2021-05-19 Dyson Technology Ltd An axial impeller
USD972706S1 (en) * 2019-02-28 2022-12-13 Ebm-Papst St. Georgen Gmbh & Co. Kg Ventilating fan
DE102019105355B4 (de) 2019-03-04 2024-04-25 Ebm-Papst Mulfingen Gmbh & Co. Kg Lüfterrad eines Axialventilators
USD972707S1 (en) * 2019-04-29 2022-12-13 Ebm-Papst Mulfingen Gmbh & Co. Kg Ventilating fan
CN115126708A (zh) * 2021-03-26 2022-09-30 全亿大科技（佛山）有限公司 叶轮及散热风扇
US11754088B2 (en) * 2021-12-03 2023-09-12 Hamilton Sundstrand Corporation Fan impeller with thin blades
US12473926B1 (en) 2024-08-14 2025-11-18 Morrison Products, Inc. Impellers and manufacturing methods thereof

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Also Published As

Publication number Publication date
EP1616101A1 (de) 2006-01-18
DE102004017727A1 (de) 2004-11-04
WO2004094835A1 (de) 2004-11-04
DE502004012310D1 (de) 2011-04-28
EP1616101B1 (de) 2011-03-16
US20060210397A1 (en) 2006-09-21
DE202004005548U1 (de) 2004-06-17
US7438522B2 (en) 2008-10-21
ATE502217T1 (de) 2011-04-15

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