EP3183459B1 - Axialventilator - Google Patents

Axialventilator Download PDF

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Publication number
EP3183459B1
EP3183459B1 EP15757450.0A EP15757450A EP3183459B1 EP 3183459 B1 EP3183459 B1 EP 3183459B1 EP 15757450 A EP15757450 A EP 15757450A EP 3183459 B1 EP3183459 B1 EP 3183459B1
Authority
EP
European Patent Office
Prior art keywords
housing
standard
diameter
axial fan
rotor
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.)
Active
Application number
EP15757450.0A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP3183459A1 (de
Inventor
Daniel Gebert
Thorsten Pissarczyk
Angelika Klostermann
Katrin Bohl
Markus ENGERT
Oliver Haaf
Marc Schneider
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
Priority to SI201531970T priority Critical patent/SI3183459T1/sl
Publication of EP3183459A1 publication Critical patent/EP3183459A1/de
Application granted granted Critical
Publication of EP3183459B1 publication Critical patent/EP3183459B1/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
    • F04D25/00—Pumping installations or systems
    • F04D25/02—Units comprising pumps and their driving means
    • F04D25/06—Units comprising pumps and their driving means the pump being electrically driven
    • F04D25/0606—Units comprising pumps and their driving means the pump being electrically driven the electric motor being specially adapted for integration in the pump
    • F04D25/0613—Units comprising pumps and their driving means the pump being electrically driven the electric motor being specially adapted for integration in the pump the electric motor being of the inside-out type, i.e. the rotor is arranged radially outside a central stator
    • F04D25/064—Details of the rotor
    • 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
    • F04D29/325—Rotors specially for elastic fluids for axial flow pumps for 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
    • F04D29/384—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
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/52—Casings; Connections of working fluid for axial pumps
    • F04D29/522—Casings; Connections of working fluid for axial pumps 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
    • F04D29/40—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
    • 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
    • F04D29/545—Ducts
    • F04D29/547—Ducts having a special shape in order to influence fluid flow
    • 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
    • F04D29/60—Mounting; Assembling; Disassembling
    • F04D29/64—Mounting; Assembling; Disassembling of axial pumps
    • F04D29/644—Mounting; Assembling; Disassembling of axial pumps 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
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
    • F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps
    • F04D29/667—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps by influencing the flow pattern, e.g. suppression of turbulence

Definitions

  • the invention relates to an axial fan for use with a wall ring plate, in particular in the field of ventilation, air conditioning and refrigeration technology.
  • Standard diameters D standard of wheels are therefore, for example, 501 mm, 562 mm, 630 mm, 707 mm, etc. A tolerance of 2% can be taken into account.
  • the axial extension of the assembly i.e. above all the fan, motor and possible additional components, the dimensioning and geometry of the fan space in the wall ring plate and the impeller itself can be changed.
  • the aim is to improve the flow mechanics of conventional axial fans in order to increase their efficiency and the air output of the motors previously used by reducing the torque requirement or to have the option of using cheaper motors with lower torque and reduced power consumption, which increase the air output in the same way delivery.
  • the efficiency can be increased by reducing the dynamic outlet losses (pressure recovery), as is the case, inter alia, in DE202010016820U1 is described.
  • a guide vane or a diffuser can be provided for an axial fan, for example.
  • such a downstream reconversion never takes place completely and is therefore less efficient compared to measures within the axial fan that lead to a reduction in the speed in the guide the impeller.
  • the hub When using external rotor motors, the hub is larger in diameter than the motor because it sits inside the hub. With axial fans, however, a large hub increases the axial speed of the flow and thus the outlet losses for the same volume flow.
  • the air performance of an axial fan can be increased by enlarging the impeller.
  • the problem here is that if the installation space is retained due to the use of a wall ring plate that is based on standards in terms of its external dimensions and an increase in the wall ring diameter for the larger impeller, there is a significant deterioration in the acoustics. Therefore, in order to holistically improve the dynamic flow, measures must already be taken in the axial fan in the area of the impeller, both to reduce the dynamic outlet losses and to maintain or even improve the acoustics.
  • the invention is therefore based on the object of providing an axial fan with improved efficiency compared with known systems and no increased noise development, which can be used as a direct replacement for an axial fan with a wall ring plate.
  • the impeller diameter is increased by a factor g compared to the standardized impeller diameter, while the external dimensions are retained, ie for D 1 and D L :
  • D 1 f ⁇ D default
  • D L G ⁇ D default
  • the invention is aimed at running wheels with diameters of 350 to 1300 mm, more preferably 500 to 910 mm.
  • the impellers themselves have 3 to 13, preferably 4 to 7 blades.
  • a stiffening web is formed which extends in the axial, radial or oblique direction, which in a favorable embodiment variant extends axially horizontally in the direction of flow or radially vertically.
  • Such a "reinforcing bead” stiffens the housing in the inflow area and stabilizes the entire assembly of fan and wall ring plate.
  • impellers that are dimensionless and strong in which the position of the static optimum efficiency lies at large values of the flow rate ⁇ and the head coefficient ⁇ , which are essentially influenced by the number of blades and the angle of inclination, are acoustically better than impellers that are dimensionlessly weak.
  • it is optimal for particularly positive acoustics if the position of the static efficiency optimum at a pressure coefficient value ⁇ (according to the ISO 5801 standard) is in a range that is defined as ⁇ ⁇ ⁇ 0.0003 ⁇ D default + 0.425 , preferably ⁇ ⁇ ⁇ 0.0003 ⁇ D default + 0.425
  • the efficiency and acoustics of the axial fan can be further improved by the formation of winglets on each of the blades of the impeller, in particular by a one-piece formation on the radial outer areas of the blades.
  • an interchangeable motor replacement insert that matches the size of the respective motor can be arranged inside the hub of the impeller. This increases the variability of the structure and reduces the costs for different models.
  • the axial fan according to the invention is not limited to the adaptation of the housing in the area of the impeller. Rather, it is provided that a diffuser is arranged in one piece on the housing in the outflow area in order to ensure pressure recovery. In a preferred embodiment, the transition of the housing from the wall ring area to the diffuser is rounded.
  • a guide vane is used in the outflow area on the housing, which vane can advantageously be retrofitted as an option.
  • a protective grid on the housing in the outflow area.
  • the protective grid can be designed as an insert in the diffuser and have meshes or rings that match in shape and size.
  • an embodiment with a one-piece impeller is favorable.
  • the blades are profiled or sickled.
  • an impeller made of plastic injection molding or die-cast aluminum is proposed as a favorable manufacturing method.
  • a low-pressure axial fan 1 with a rectangular wall ring plate 9 formed in one piece with the side edge lengths D_2 and D_1 (D1 ⁇ D2) is shown in a front view, the plan view offering a view in the direction of flow and with five impeller blades extending radially outwards from the hub 6 2 trained impeller 20 in the center of the axial fan 1 can be seen.
  • the annular wall plate 9 has standard dimensions and, together with the axial fan 1, forms a structural unit that enables direct exchange with existing systems, for example in condensers, heat exchangers, refrigeration systems and the like.
  • FIG 2 shows one half of the axial fan 1 in a three-dimensional, partially sectioned view. It goes without saying that the half opposite the axial center line is mirrored and identical in design.
  • the axial fan 1 comprises a motor 8 designed as an external rotor, which is arranged inside the hub 6 and is connected to the impeller 20 via a motor replacement insert 7 that matches the dimensions of the motor 8 .
  • the motor replacement insert 7 can be detachably attached to the hub 6 .
  • the motor 8 drives the hub 6 and thus the impeller 20 via the motor interchangeable insert 7 .
  • the housing 10 of the axial fan 1 has, seen in the direction of flow from left to right, an inflow area 11 with the maximum external housing dimension D_1, a tapered section 4 with a partially elliptically curved cross section, a central section 14 that extends axially horizontally, and a central section 14 that is designed with a diffuser 3 Outflow area 12 on.
  • the opening angle "alpha" of the diffuser 3 is about 12 degrees.
  • the overall axial length of the axial fan 1 is marked with h.
  • the impeller 20 is arranged in the axial fan 1 essentially at the level of the middle section 14, with a vertical plane at the boundary between the middle section 14 and the diffuser 3 intersecting the impeller 20 in the radial direction. At its radial end section, each blade 2 of the impeller 20 has a winglet 21 which extends along the axial outer edge.
  • the impeller 20 also has an enlarged impeller diameter D_L compared to an impeller diameter D_standard based on DIN 323 or ISO 3, so that the ratio of D_1/D_L is smaller than the ratio of D_1/D_standard. Due to the increase in diameter of the impeller 20 compared to the standardized impeller diameter D_standard, the exit surface of the axial fan 1 increases, which reduces its dynamic exit losses and increases efficiency. In the embodiment shown, the impeller diameter D_L is approx. 10% larger than the standardized impeller diameter D_standard.
  • an outer edge area 5 is formed on the inflow side, which extends from the housing outer diameter D_1 to the inflow diameter D_A radially perpendicularly over a length c/2 and is adjoined by the narrowing section 4 viewed in the axial flow direction.
  • the radial length c of the outer edge area 5 results from the difference between the outer housing dimension D_1 and the definable inflow diameter D_A.
  • the axial width b and radial length a of the tapering section 4 form a ratio of a/b which, in the embodiment shown, corresponds approximately to the value 0.5.
  • the lengths a and b are measured, taking into account the wall thickness of the housing 10.
  • the length b ends at the point at which the housing 10 is completely in the horizontal middle section 14 merges, ie no arc shape of the tapering section 4 can be detected.
  • the length a ends at the point at which the housing 10 merges into the completely vertical outer edge region 5, ie the tapered section 4 is no longer in an arc shape.
  • the axial end of the tapered section 4 in the direction of flow forms a vertical plane which in the embodiment shown essentially coincides with the front edge of the hub 6 .
  • figure 3 shows an execution according to figure 2 alternative embodiment in which all the features are identical, but on the housing 10 of the axial fan 1 in the inflow area 11 between, i.e. in the transition from the outer edge area 5 to the tapering section 4, a stiffening web 13 extending horizontally in the axial direction is additionally formed to stiffen the inflow area 11 is.
  • the dimension a of the tapered section 4 can be determined even more easily, since it extends to the axial inside of the axially horizontal stiffening web 13 .
  • figure 4 shows the reduction in the pressure coefficient ⁇ of the axial fan 1 according to the invention compared to those of the prior art based on the standardized impeller diameter D_standard.
  • the static optimum efficiency of the axial fan 1 according to the invention is surprisingly at a pressure coefficient value ⁇ 0.0003 ⁇ D_standard+0.425, ie at or below the limit curve drawn in the diagram, whereas the impellers according to the prior art with and without guide vane are always above the limit curve .
  • the implementation of the invention is not limited to the preferred exemplary embodiments specified above. Rather, a number of variants are conceivable which make use of the solution shown even in the case of fundamentally different designs.
  • the number of blades of the impeller is not limited to five, but can be in the range of 3 to 13, in particular 4 to 7.
  • a guide vane (not shown in the figures) can be used to optimize the flow, and a protective grid can be used to protect against accidental contact.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
EP15757450.0A 2014-08-18 2015-08-13 Axialventilator Active EP3183459B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
SI201531970T SI3183459T1 (sl) 2014-08-18 2015-08-13 Aksialni ventilator

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102014111767.0A DE102014111767A1 (de) 2014-08-18 2014-08-18 Axialventilator
PCT/EP2015/068646 WO2016026762A1 (de) 2014-08-18 2015-08-13 Axialventilator

Publications (2)

Publication Number Publication Date
EP3183459A1 EP3183459A1 (de) 2017-06-28
EP3183459B1 true EP3183459B1 (de) 2023-08-02

Family

ID=54056167

Family Applications (1)

Application Number Title Priority Date Filing Date
EP15757450.0A Active EP3183459B1 (de) 2014-08-18 2015-08-13 Axialventilator

Country Status (7)

Country Link
US (1) US11365741B2 (hu)
EP (1) EP3183459B1 (hu)
CN (1) CN207080384U (hu)
DE (2) DE102014111767A1 (hu)
HU (1) HUE063340T2 (hu)
SI (1) SI3183459T1 (hu)
WO (1) WO2016026762A1 (hu)

Families Citing this family (11)

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Publication number Priority date Publication date Assignee Title
JP6363811B1 (ja) * 2017-09-29 2018-07-25 アイリスオーヤマ株式会社 サーキュレータ
CN108716473B (zh) * 2018-03-02 2020-12-29 青岛海信日立空调系统有限公司 一种轴流风扇和空调器室外机
DE102018128792A1 (de) * 2018-11-16 2020-05-20 Ebm-Papst Mulfingen Gmbh & Co. Kg Kompakter Diagonalventilator mit Nachleiteinrichtung
DE102018132002A1 (de) * 2018-12-12 2020-06-18 Ebm-Papst Mulfingen Gmbh & Co. Kg Ventilationseinheit
CN109441876B (zh) * 2018-12-26 2023-12-29 浙江科贸智能机电股份有限公司 一种无蜗壳后向离心通风机
JP2020106024A (ja) * 2018-12-27 2020-07-09 三星電子株式会社Ｓａｍｓｕｎｇ Ｅｌｅｃｔｒｏｎｉｃｓ Ｃｏ．，Ｌｔｄ． 送風装置、熱交換ユニット及び空気清浄ユニット
IT201900007935A1 (it) * 2019-06-04 2020-12-04 R E M Holding S R L Ventilatore con virola migliorata
USD972120S1 (en) * 2019-12-03 2022-12-06 Ebm-Papst Mulfingen Gmbh & Co. Kg Ventilation unit
CN111878457B (zh) * 2020-07-23 2023-09-08 珠海格力电器股份有限公司 具有降低噪音的送风组件及空调系统
US11391286B2 (en) * 2020-10-02 2022-07-19 Therma-Stor LLC Portable blower fan assembly
DE102022129987B3 (de) 2022-11-14 2024-03-14 Bayerische Motoren Werke Aktiengesellschaft Strömungsmaschine, insbesondere für ein Kraftfahrzeug, sowie Kraftfahrzeug mit einer solchen Strömungsmaschine

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Also Published As

Publication number Publication date
CN207080384U (zh) 2018-03-09
SI3183459T1 (sl) 2023-11-30
HUE063340T2 (hu) 2024-01-28
US11365741B2 (en) 2022-06-21
EP3183459A1 (de) 2017-06-28
WO2016026762A1 (de) 2016-02-25
DE202015009320U1 (de) 2017-02-08
US20170152854A1 (en) 2017-06-01
DE102014111767A1 (de) 2016-02-18

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