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.
• D standard ⁇ nl x standard diameter
• Dstandard of wheels are thus for example 501 mm, 562 mm, 630 mm, 707 mm, etc. A tolerance of 2% can be considered.
• the axial extent of the assembly i. especially the fan, motor and possible additional components, the dimensioning and geometry of the
• the flow mechanics of conventional axial fans is to be improved in order to increase their efficiency and the air performance of the previously used engines by reducing the torque requirement or, in order to have the opportunity to use cheaper engines with lower torque and reduced power consumption, the air flow in deliver the same way.
• the efficiency can be increased by reducing the dynamic exit losses (pressure recovery), as described, inter alia, in DE202010016820U1.
• pressure recovery pressure recovery
• an idler or a diffuser can be provided in an axial fan, for example.
• such a downstream conversion never happens completely and is thus inefficient compared to measures within the axial fan, which leads to a reduction of the speed in the Run impeller.
• the hub When using external rotor motors, the hub is larger in diameter than the motor because it sits inside the hub. For axial fans, however, a large hub increases the axial velocity of the flow and thus the outlet losses at the same volume flow.
• the air output of an axial fan can be increased by increasing the size of the impeller.
• the problem here is, however, that there is a significant deterioration in the acoustics when maintaining the space due to the use of fixed in their outer dimensions to standards wall ring plate and an increase in the wall ring diameter for the enlarged impeller.
• measures must therefore 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 an object of the invention to provide an axial fan with respect to known systems improved efficiency at not increased noise, which can be used as a direct replacement of an axial fan with wall ring plate.
• This object is achieved by the feature combination according to claim 1.
• an axial fan in particular a low-pressure axial fan, proposed for use with a wall-ring plate, comprising a motor, a housing with inflow and outflow and an impeller driven by the motor, wherein the housing
• the inflow side has a housing outside diameter Di and the impeller an opposite one based on a DIN or ISO standard, in particular the DIN 323 and ISO 3 standard impeller diameter D s t enlarged to dard impeller diameter D L, so that a ratio of DI / DL is smaller than a ratio of Di / D s standard
• Einström inflow and seen in the flow direction seen from an inflow diameter D A on a wall ring diameter DWR in cross-section narrowing tapering section, the axial width b and radial length a a ratio of a / b in a range of 0.3 to 0.7 , preferably from 0.4 to 0.6, more preferably 0.5.
• the arcuate shape thus forms in a favorable embodiment in the lateral cross-section part of an oval, more preferably a part of an ellipse.
• the combination of an increase of the impeller diameter D L over the standardized impeller diameter while adjusting the Einströmgeometrie provides the desired reduced torque requirement with a non-deteriorated acoustics.
• Impeller diameter enlargement increases the exit area, resulting in a reduction of the dynamic leakage losses and an associated increase in efficiency.
• the possibility of enlarging the impeller while maintaining the good acoustic behavior is achieved by the Einströmgeometrie described above.
• the factors g and f are defined in a range g min to g max and in a range f min to f max according to the invention
• the invention is directed to wheels with diameters of 350 to 1300mm, more preferably 500 to 9 0mm.
• the wheels themselves have 3 to 3, preferably 4 to 7 blades on.
• a reinforcing web extending in the axial, radial or oblique direction to be formed between the outer edge region and the narrowing section and, in a favorable embodiment, extend axially horizontally in the flow direction or radially perpendicularly.
• Such a “stiffening bead” stiffens the housing in the inflow area and stabilizes the entire assembly of fan and wall ring plate.
• dimensionless strong impellers in which the position of the static efficiency optimum lies at large values of the flow rate ⁇ and the pressure factor im which are essentially influenced by the number of blades and the angular position, are acoustically better than dimensionless weak impellers.
• the position of the static efficiency optimum at a value of the pressure factor ⁇ (according to standard ISO 5801) lies in a range which is defined as
• the efficiency and acoustics of the axial fan can be further improved by forming winglets on each of the blades of the impeller, in particular by integrally forming them on the radial outer portions of the blades.
• the invention provides that within the hub of the impeller an interchangeable, in size to the respective motor matching engine replacement insert can be arranged. This increases the variability of the design 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 region of the impeller. Rather, it is provided that in the outflow to the housing integrally a diffuser is arranged to ensure the pressure recovery.
• the transition of the housing from the wall-ring area to the diffuser is rounded off in a preferred embodiment. It is also advantageous if, for comparatively high back pressures in the axial fan according to the invention in the discharge area on the housing, a Nachleitrad is used, which is conveniently optional retrofitted.
• a protective grid in the discharge area on the housing.
• the protective grid can be designed as an insert in the diffuser and have matching meshes or rings in shape and size.
• an embodiment with a one-piece impeller is low.
• a blade training is provided according to the invention in an advantageous embodiment, that these are profiled or insichelt.
• Fig. 1 is a front view of an axial fan with wall ring plate
• Fig. 2 is a three-dimensional, partially sectioned view of a
• Fig. 3 shows an alternative embodiment of the axial fan of Fig. 2;
• Fig. 4 is a diagram of the pressure achieved according to the invention.
• FIG. 1 shows a front view of a low-pressure axial fan 1 with a rectangular wall-ring plate 9 formed integrally thereon with the side edge lengths D_2 and D_1 (D1 ⁇ D2), the plan view providing a view in the flow direction and that with five extending radially from the hub 6 outwardly extending impeller blades 2 trained impeller 20 can be seen in the center of the axial fan 1.
• the wall ring plate 9 has standard dimensions and forms with the axial fan 1, a structural unit, which allows a direct exchange with existing systems, for example in condensers, heat exchangers, refrigeration systems and the like.
• Figure 2 shows one half of the axial fan of Fig. 1 in a three-dimensional, partially sectioned view. It is understood that the axial center line opposite half mirrored identically formed.
• 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 changeover insert 7 that is suitable for the dimension of the motor 8.
• the engine replacement insert 7 may be releasably secured to the hub 6.
• the motor 8 drives the hub 6 and thus the impeller 20 via the motor changeover insert 7.
• the housing 10 of the axial fan 1 has seen in the flow direction from left to right an inflow region 1 1 with maximum
• Housing outer dimension D_1 a partially sectionally bent in the cross-section tapered portion 4, an axially horizontally extending central portion 14 and one with a diffuser 3 formed Outflow 12 on.
• the opening angle "alpha" of the diffuser 3 is approximately 2 degrees, and the axial total length of the axial fan 1 is designated h
• the impeller 20 is arranged in the axial fan 1 essentially at the level of the central portion 14, with a vertical plane at the boundary between the impeller 20 radially intersects the middle section 14 and the diffuser 3.
• Each blade 2 of the impeller 20 has at its radial end section a winglet 21 extending along the axial outer edge.
• the impeller 20 further has an impeller diameter D_L which is larger than that based on DIN 323 or ISO 3 standardized impeller diameter D_standard, so that the ratio of
• D_1 / D_L is less than the ratio of D_1 / D_standard.
• the impeller diameter D_L is about 10% larger than the standardized impeller diameter D_standard.
• the radial length c of the outer edge region 5 results from the difference between the housing outer 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 in the fully constantly horizontal middle section 14 passes, ie no arch shape of the tapering section 4 is more noticeable.
• the length a ends at the point at which the housing 10 merges into the completely vertical outer edge region 5, ie, no arched shape of the tapering section 4 can be detected any longer.
• the axial end of the tapering section 4 in the flow direction forms a vertical plane, which coincides in the embodiment shown substantially with the front edge of the hub 6.
• FIG. 3 shows an alternative embodiment to that according to FIG. 2, in which all features are identical, but in addition to the housing 10 of the axial fan 1 in the inflow region 11, between, i. in the transition from the outer edge region 5 to the tapering section 4, a stiffening web 3 extending horizontally in the axial direction is formed for stiffening the inflow region 11.
• the dimension a of the tapering section 4 can be determined even more simply, since it extends to the axial inside of the axially horizontal stiffening web 13.
• FIG. 4 shows the reduction of the pressure factor ⁇ of the axial fan 1 according to the invention compared to those of the prior art with reference to the standardized impeller diameter D_standard.
• the static efficiency optimum of the axial fan 1 according to the invention surprisingly lies at a pressure value i J ⁇ -0.0003 ⁇ D_standard + 0.425, ie at or below the limit curve shown in the diagram, whereas the prior art wheels with and without follower wheel are always above the limit curve lie.
• the invention is not limited in its execution to the above-mentioned preferred embodiments. Rather, a number of variants is conceivable, which makes use of the illustrated solution even with fundamentally different types of use.
• the number of blades of the impeller is not limited to five, but may be in the range of 3 to 13, especially 4 to 7.
• a Nachleitrad not shown in the figures for flow optimization and a protective grid can be used as contact protection.

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)

Priority Applications (1)

Applications Claiming Priority (2)

Publications (2)

Family

ID=54056167

Family Applications (1)

Country Status (7)

Families Citing this family (15)

Family Cites Families (29)

• 2014
  • 2014-08-18 DE DE102014111767.0A patent/DE102014111767A1/de not_active Withdrawn
• 2015
  • 2015-08-13 CN CN201590000721.0U patent/CN207080384U/zh not_active Expired - Fee Related
  • 2015-08-13 DE DE202015009320.5U patent/DE202015009320U1/de not_active Expired - Lifetime
  • 2015-08-13 EP EP15757450.0A patent/EP3183459B1/fr active Active
  • 2015-08-13 WO PCT/EP2015/068646 patent/WO2016026762A1/fr not_active Ceased
  • 2015-08-13 US US15/325,782 patent/US11365741B2/en active Active
  • 2015-08-13 SI SI201531970T patent/SI3183459T1/sl unknown
  • 2015-08-13 HU HUE15757450A patent/HUE063340T2/hu unknown

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