EP3705727A1 - Lüfterrad eines axialventilators - Google Patents

Lüfterrad eines axialventilators Download PDF

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Publication number
EP3705727A1
EP3705727A1 EP20158943.9A EP20158943A EP3705727A1 EP 3705727 A1 EP3705727 A1 EP 3705727A1 EP 20158943 A EP20158943 A EP 20158943A EP 3705727 A1 EP3705727 A1 EP 3705727A1
Authority
EP
European Patent Office
Prior art keywords
fan wheel
blade
fan
projection
blade edge
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
EP20158943.9A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP3705727B1 (de
Inventor
Oliver Haaf
Thorsten Pissarczyk
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 Mulfingen GmbH and Co KG
Original Assignee
Ebm Papst Mulfingen GmbH and Co KG
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 Mulfingen GmbH and Co KG filed Critical Ebm Papst Mulfingen GmbH and Co KG
Publication of EP3705727A1 publication Critical patent/EP3705727A1/de
Application granted granted Critical
Publication of EP3705727B1 publication Critical patent/EP3705727B1/de
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
    • F04D29/32—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
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D19/00—Axial-flow pumps
    • F04D19/002—Axial flow fans
    • 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
    • F04D29/388—Blades characterised by construction
    • 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
    • F04D29/52—Casings; Connections of working fluid for axial pumps
    • F04D29/54—Fluid-guiding means, e.g. diffusers
    • F04D29/541—Specially adapted for elastic fluid pumps
    • F04D29/542—Bladed diffusers
    • 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
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
    • F04D29/68—Combating cavitation, whirls, noise, vibration or the like; Balancing by influencing boundary layers
    • F04D29/681—Combating cavitation, whirls, noise, vibration or the like; Balancing by influencing boundary layers 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
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2240/00—Components
    • F05B2240/20—Rotors
    • F05B2240/30—Characteristics of rotor blades, i.e. of any element transforming dynamic fluid energy to or from rotational energy and being attached to a rotor
    • F05B2240/301—Cross-section characteristics
    • 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
    • F05D2240/304—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 trailing edge of a rotor blade
    • 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 fan wheel of an axial fan with a plurality of fan wheel blades arranged around an axis of rotation in a blade ring.
  • Fan wheels of the generic type of axial fans for generating an axial air flow have been known for a long time and usually comprise a plurality of fan wheel blades which, starting from the hub, extend radially outward and are arranged in a blade ring.
  • the invention is therefore based on the object of providing a fan wheel that ensures a reduction in the sound level generated during operation, in particular in such disturbed installation situations.
  • a fan wheel of an axial fan with several fan wheel blades arranged around an axis of rotation in a blade ring in which at least one of the fan wheel blades has a radially inner section and a blade edge section directly adjoining the inner section and adjoining a blade edge.
  • the at least one fan wheel blade has a local projection over a radial extent of the blade edge section, which is formed as an extension of the chord length of the fan wheel blade and locally enlarges the fan wheel blade in the blade edge section.
  • the blade edge section is thus delimited from the inner section and defined in that the projection is always provided. It is also essential to the invention that a mean angle of attack of the fan wheel blade, in particular in the blade edge section, with respect to a plane of rotation of the fan wheel is greater than a mean angle of attack of the projection with respect to the plane of rotation.
  • a preferred embodiment variant provides that the mean angle of attack of the projection with respect to the plane of rotation of the fan wheel has a value between 1-15 °, more preferably between 3-10 °.
  • the angle of attack of the projection is always smaller than that of the fan impeller blade in the area outside the projection.
  • fan impellers of axial fans use a ring that surrounds the impeller blades radially on the outside, which is often referred to as a centrifugal ring.
  • an advantageous embodiment of the fan wheel of the present disclosure is specifically directed to the fan wheel blades ending freely at their respective radial blade edges and being free from connection, i. that no ring or the like connects the impeller blades.
  • the free end the radially outer blade edges of the impeller blades are not influenced in terms of flow, so that the effect of the projection is beneficial.
  • the blade edge section of the at least one fan wheel blade adjoining the blade edge is determined in a radial outer region of the fan wheel blade.
  • the size of this radial outer area and thus the radial extent of the projection is defined by the ratio of the radius LS of the fan wheel blade up to the blade edge section to the maximum radius of the fan wheel blade LD such that 0.7 LS / LD 1, preferably 0.85 LS / LD ⁇ 0.95.
  • the chord length of the fan wheel blade in a direction perpendicular to the axis of rotation is locally increased relative to the inner section such that 1.05 L1 / L2 1 applies, 4, more preferably 1.1 L1 / L2 1.3, where L1 is the maximum chord length of the fan wheel blade in the blade edge section and L2 is the chord length of the fan impeller blade at the boundary between the inner section and the blade edge section, in each case measured at the radially outer blade edge of the fan wheel blade.
  • the fan impeller blades each have a leading edge and a trailing edge. A particularly advantageous effect for noise reduction is achieved if the projection is formed on the blade leading edge.
  • the blade trailing edge in turn, has a convexly rounded, arched course in a favorable embodiment.
  • the blade leading edge is also preferably curved in an arc shape, but with a larger, in particular many times larger, radius than the blade trailing edge.
  • an embodiment of the fan wheel is advantageous in which the projection is formed in one piece with the fan wheel blade.
  • the fan wheel is preferably made of plastic, so that all technical features influencing the flow are integrally formed in the fan wheel blades.
  • the projection has a tip pointing in the circumferential direction.
  • the tip is preferably spaced radially inward relative to a maximum outer radius of the fan wheel blade. This means that the projection is designed to be drawn in radially inward, but the tip preferably defines an imaginary circle during operation which is spaced apart from the outer radius of the fan wheel.
  • an embodiment variant of the fan wheel is advantageous in which the tip of the projection in the blade edge section is offset radially outwards off-center.
  • the projection is formed in such a way that its tip pointing in the circumferential direction is closer to the outer radius than to the inner section of the fan wheel blade.
  • a configuration of the impeller blades in which the tip of the projection is rounded off also has a flow-technical and noise-reducing effect on the fan wheel.
  • the fan wheel blades each have a winglet on their radially outer blade edge.
  • a winglet is defined as a design on the fan wheel blade in which a thickening or rounding from the bottom to the top is provided on the radial end of the fan wheel blade.
  • brushes can also be provided on the radially outer edge of the blade.
  • the fan wheel blades at least along the projection, have a smaller average blade thickness than in the remaining area of the respective fan wheel blade.
  • the fan wheel blades are preferably designed in such a way that they each define a radial central region around their radial center, in which the chord length of the fan wheel blade has a maximum.
  • the central area extends preferably up to 30% of the radial maximum extent of the fan wheel blade around its radial center.
  • fan wheel is preferred in which all fan wheel blades are of identical design.
  • the disclosure further includes an axial fan with a fan wheel described above.
  • FIGS. 1 - 5 show an embodiment of a fan wheel 1 of an axial fan, in which five identical fan wheel blades 2 extend radially outward starting from the hub 17 and form a ring of blades around the axis of rotation RA.
  • the number of fan wheel blades 2 is set to five merely by way of example, but can also be higher or lower in alternative embodiments.
  • Each fan wheel blade 2 has a blade trailing edge 8, a blade leading edge 9 and a radial blade edge 5 which ends freely.
  • the individual fan impeller blades 2 are connected exclusively via the hub 17.
  • the blade leading edges 8 are convexly rounded in the circumferential direction and each determine an arcuate course, the blade leading edges 9 extending from the hub 17 essentially in a straight line radially outward.
  • the fan impeller blades 2 are clearly seen to be arched and inclined with respect to the plane of rotation RE.
  • Stiffening ribs 25 aligned in the circumferential direction are formed on their respective axial underside, some of which extend as far as the hub 17 and are connected to it over a predetermined axial extent.
  • the fan impeller blades 2 each have an inner section 3 lying radially on the inside and a blade edge section 4 which, viewed in the radial direction, directly adjoins the inner section 3 and extends to the respective blade edge 5.
  • the boundary 13 between the inner section 3 and the blade edge section 4 is shown in FIG Figure 1 entered a dashed line.
  • the radially outwardly lying blade edge section 4 is defined in the fan wheel blades 2 in that it has the local protrusion 6 over its radial extent, which locally increases the chord length of the respective fan wheel blade 2 in the blade edge section 4 in the circumferential direction.
  • the boundary 13 is thus defined at the point at which the projection 6 begins.
  • the projection 6 is embodied on the respective blade leading edges 9 in an essentially triangular basic shape which has a rounded tip 10 pointing in the circumferential direction.
  • a line is identified by the reference numeral 12 which shows the position of the tip 10 parallel to the blade edge 5.
  • the tip 10 of the projection 6 is spaced radially inwardly in relation to a maximum outer radius of the fan wheel blade 2 and is thus offset radially outwardly off-center in the radial direction in the blade edge section 4. This is achieved by different angular profiles of the outer edges of the projection 6, which are formed on the one hand by the blade leading edge 9 and on the other hand by the blade edge 5.
  • each setting angle along the fan wheel blade 2 with respect to the plane of rotation RE is always smaller than each setting angle along the projection 6 with respect to the plane of rotation RE.
  • the total angle of incidence ⁇ of the fan impeller blade 2 is shown along the chord length L in the central area MB around the radial center, which connects the edge point XV1 on the blade trailing edge 8 with the edge point XV2 on the blade leading edge 9.
  • the chord length L has its maximum in the central area MB.
  • the projection 6 is formed in one piece on the fan impeller blade 2, but its extension and the resulting chord lengthening can be clearly determined and delimited by the abrupt change in the course of the blade leading edge 9.
  • Alternative designs provide that the projection is attached as an attachment to the respective fan wheel blade.
  • the projection 6 in the blade edge section 4 assumes a radial extent which is determined by the ratio LS / LD, which in the case shown is 0.88.
  • LS is the radius of the fan wheel blade 2 up to the blade edge section 4, LD the maximum outer radius of the fan wheel blade 2.
  • the ratio LS / LD should be between 0.7-1, in particular between 0.85-0.98.
  • the size of the projection 6 in the circumferential direction is determined by the different chord lengths.
  • the chord length of the fan impeller blade 2 is increased by the projection 6 in the direction perpendicular to the axis of rotation RA such that the ratio of the maximum chord length L1 of Fan wheel blade 2 including the projection 6 for the chord length L2 of the fan wheel blade 2 without the projection 6 is 1.2.
  • the ratio should be set between 1.05-1.3, in particular between 1.1-1.2.
  • the blade thickness of the projection 6 can optionally be greater than the blade thickness of the remaining fan wheel 2, as in FIG Figure 4 shown.
  • Figure 6 shows the advantages achieved by the design of the fan wheel 2 according to the invention for reducing the sound pressure level Lp at the different frequencies f
  • the solid line 77 showing the result of the wheel 2 according to FIG Figure 1
  • the dashed line 88 identifies an identical impeller without a projection 6.
  • the sound pressure level can be reduced significantly over the entire frequency curve, but especially at very low frequencies.
  • the Figure 7 shows a comparison of the ratio of the angle of attack ⁇ to the maximum angle of attack p_max of the fan impeller blade 2 with the projection 6 from FIG Figure 1 over the radial course of the radius r to the maximum radius r_max compared to the prior art (dashed line) without a projection.
  • the falling angle of attack at the beginning of the blade edge section 4 at a ratio r / r_max of 0.9 can be clearly seen.
  • Figure 8 shows a diagram of the chord length L to the maximum chord length L_max of the fan wheel blade 2 with the projection 6 from Figure 1 over the radial course of the radius r to the maximum radius r_max compared to the prior art (dashed line) without a projection.
  • the maximum of the chord length is 0.7 of the total radial extension of the fan impeller blade 2. In the blade edge section 4, the chord length increases locally around the projection 6.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
EP20158943.9A 2019-03-04 2020-02-24 Lüfterrad eines axialventilators Active EP3705727B1 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102019105355.2A DE102019105355B4 (de) 2019-03-04 2019-03-04 Lüfterrad eines Axialventilators

Publications (2)

Publication Number Publication Date
EP3705727A1 true EP3705727A1 (de) 2020-09-09
EP3705727B1 EP3705727B1 (de) 2024-08-07

Family

ID=69726469

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20158943.9A Active EP3705727B1 (de) 2019-03-04 2020-02-24 Lüfterrad eines axialventilators

Country Status (4)

Country Link
US (1) US11248623B2 (zh)
EP (1) EP3705727B1 (zh)
CN (2) CN210265263U (zh)
DE (1) DE102019105355B4 (zh)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
USD972119S1 (en) * 2018-11-28 2022-12-06 Ebm-Papst Mulfingen Gmbh & Co. Kg Fan
USD971398S1 (en) * 2019-03-04 2022-11-29 Ebm-Papst Mulfingen Gmbh & Co. Kg Fan wheel of an axial fan
USD980409S1 (en) * 2019-03-07 2023-03-07 Ziehl-Abegg Se Fan wheel
WO2024086324A1 (en) * 2022-10-21 2024-04-25 Texas Tech University System Aircraft with ducted propulsion

Citations (5)

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WO1996016272A1 (en) * 1994-11-18 1996-05-30 Itt Automotive Electrical Systems, Inc. Fan blade with curved planform and high-lift airfoil having bulbous leading edge
WO2009019559A1 (en) * 2007-08-07 2009-02-12 Spal Automotive S.R.L. Axial flow fan
JP2014062534A (ja) * 2012-09-24 2014-04-10 Denso Corp 送風機
EP3029336A1 (de) * 2014-12-03 2016-06-08 ebm-papst Mulfingen GmbH & Co. KG Schaufel eines ventilatorrades, ventilatorrad und axialventilator

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1991007593A1 (en) * 1989-11-16 1991-05-30 Airflow Research And Manufacturing Corporation Multi-sweep blade with abrupt sweep transition
WO1996016272A1 (en) * 1994-11-18 1996-05-30 Itt Automotive Electrical Systems, Inc. Fan blade with curved planform and high-lift airfoil having bulbous leading edge
WO2009019559A1 (en) * 2007-08-07 2009-02-12 Spal Automotive S.R.L. Axial flow fan
JP2014062534A (ja) * 2012-09-24 2014-04-10 Denso Corp 送風機
EP3029336A1 (de) * 2014-12-03 2016-06-08 ebm-papst Mulfingen GmbH & Co. KG Schaufel eines ventilatorrades, ventilatorrad und axialventilator

Also Published As

Publication number Publication date
CN111649000A (zh) 2020-09-11
CN210265263U (zh) 2020-04-07
EP3705727B1 (de) 2024-08-07
DE102019105355A1 (de) 2020-09-10
DE102019105355B4 (de) 2024-04-25
US11248623B2 (en) 2022-02-15
US20200284268A1 (en) 2020-09-10

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