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EP2823184B1 - Ventilateur axial - Google Patents

Ventilateur axial Download PDF

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Publication number
EP2823184B1
EP2823184B1 EP13711568.9A EP13711568A EP2823184B1 EP 2823184 B1 EP2823184 B1 EP 2823184B1 EP 13711568 A EP13711568 A EP 13711568A EP 2823184 B1 EP2823184 B1 EP 2823184B1
Authority
EP
European Patent Office
Prior art keywords
strut
motor
housing
strut parts
parts
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
EP13711568.9A
Other languages
German (de)
English (en)
Other versions
EP2823184A2 (fr
Inventor
Omar Sadi
Andreas Gross
Lothar Ernemann
Frieder Lörcher
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.)
Ziehl Abegg SE
Original Assignee
Ziehl Abegg SE
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 Ziehl Abegg SE filed Critical Ziehl Abegg SE
Priority to SI201332055T priority Critical patent/SI2823184T1/sl
Publication of EP2823184A2 publication Critical patent/EP2823184A2/fr
Application granted granted Critical
Publication of EP2823184B1 publication Critical patent/EP2823184B1/fr
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
    • 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
    • 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
    • F04D29/54—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
    • F04D29/60—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
    • F04D29/60—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
    • F04D29/646—Mounting or removal of 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
    • F04D29/66—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
    • F04D29/666—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps by means of rotor construction or layout, e.g. unequal distribution of blades or vanes
    • 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
    • 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
    • F05D2230/00—Manufacture
    • F05D2230/10—Manufacture by removing material
    • 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
    • F05D2230/00—Manufacture
    • F05D2230/50—Building or constructing in particular ways
    • F05D2230/51—Building or constructing in particular ways in a modular way, e.g. using several identical or complementary parts or features
    • 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
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T29/00—Metal working
    • Y10T29/49—Method of mechanical manufacture
    • Y10T29/49316—Impeller making
    • Y10T29/49336—Blade making

Definitions

  • the invention relates to an axial fan according to the preamble of claim 1.
  • Axial fans are used for a wide variety of applications. Although axial fans have sufficient overall efficiency and low flow resistance, there are more and more applications where even higher requirements are placed on overall efficiency and/or flow resistance.
  • Axial fans are known ( DE 25 29 541 B2 ), in which the motor is attached to the housing via a suspension.
  • the suspension is provided by radially extending struts extending between a stator hub and the housing.
  • the struts are arranged approximately on edge in the flow direction of the air and are curved over their height. Since the struts are continuous over their length and height, the flow resistance is still too high.
  • the struts also lead to an increase in the weight of the axial fan and contribute to the generation of noise during the operation of the axial fan.
  • the motor is attached to the housing by means of webs.
  • the webs are also continuous and extend transversely to the flow direction of the air, resulting in a high flow resistance and a corresponding weight of the axial fan, as well as a loud operating noise.
  • Axial fans are also known ( DE 10 2011 015 784 A1 ), in which the motor is connected to the housing via approximately radial struts.
  • the struts are designed as guide vanes and are arranged approximately on edge. They are also solid throughout.
  • the motor is connected to the housing via radial struts.
  • the struts are widened.
  • the struts also lead to a high flow resistance, to a high weight of the axial fan and to a noise development when the axial fan is in operation.
  • a fan is also known ( GB 2 281 102 A ), whose motor is connected to a housing via a suspension.
  • the suspension includes diametrically opposed struts extending radially from an engine mount, the outer ends of which have fasteners bent at right angles for attachment to the inside of the housing.
  • the struts are each formed by two adjacent strut elements, of which one strut element has an opening and the other strut element has a projection filling the opening.
  • the motor is housed in a cylindrical housing supported by three flexible support arms attached to a bulkhead or other suitable support structure.
  • the support arms are each provided with a recess in order to adjust the spring properties of the support arms.
  • the invention is based on the object of designing the axial fan of the generic type in such a way that the axial fan has a high overall efficiency and only a low flow resistance.
  • the axial fan should only have a low weight, be able to be produced inexpensively and, in particular, generate little noise during operation.
  • the axial fan according to the invention is characterized in that at least part of the strut part is provided over a part of its length with at least one recess formed by a punching in the flat material.
  • the flow resistance through the strut part is minimized by the recess.
  • the shape and/or size and/or position of the recess can be adapted to the operating conditions of the axial fan, so that the optimal flow resistance can be set depending on the application.
  • the recess in the strut part means that the weight of the axial fan is kept low. The more strut parts that are used as a suspension, the greater the weight reduction of the axial fan compared to axial fans with struts formed continuously over the length and height.
  • the generation of noise from the axial fan according to the invention is greatly reduced because the size of turbulent separation areas is greatly reduced as a result of the recess. Since the strut part is also arranged approximately upright in the flowing air is, the flow resistance can be kept to a minimum in conjunction with the size and/or shape and/or position of the recess.
  • the strut part is formed by a sheet metal part.
  • the use of sheet metal results in low manufacturing costs for the axial fan.
  • the sheet metal part can be easily deformed if required for installation. It is easy to assemble and disassemble. In particular, it is not necessary to weld this sheet metal part at its ends, but its ends can be screwed, riveted or the like to the corresponding components of the axial fan.
  • the recess can be produced very simply by stamping.
  • the legs of the strut part delimiting the recess are advantageously designed with a width which corresponds to approximately 3 to 15 times the flat material thickness, preferably 5 times the flat material thickness.
  • the recess is formed by punching out the flat material.
  • the recess in the strut part is designed in such a way that at least one support part protrudes from at least one edge of the recess. It is thus possible, for example, to introduce a U-shaped punching in a metal sheet and to bend the sheet metal part located between the edges of the punching out of the plane of the sheet metal. In this way the support part is formed, which protrudes from the strut part and is advantageously formed in one piece with it. In this way, the strut part can be provided with one or more support parts, which also significantly increase the stability of the strut part and thus also of the entire axial fan.
  • Both recesses with such a transversely projecting support part and recesses with a peripheral edge can be provided on a strut part.
  • a non-claimed axial fan can have several strut parts, which can be provided in a rotationally symmetrical arrangement. In this way, the motor can be optimally supported on the housing.
  • a pot can be provided to accommodate the motor, to which the inner end of the strut part is attached.
  • this pot can be cylindrical or tubular or even angular. It is also possible to make the pot U-shaped so that it has no surrounding wall. The motor can then be suitably mounted in the U-shaped pot. The strut parts can also be easily mounted on a pot designed in this way.
  • the axial fan can be designed in such a way that the motor is suspended by guide vanes, which are located behind the impeller in the direction of flow of the air.
  • the engine mounting thus has the function of a guide wheel, with which an additional increase in efficiency is achieved.
  • This axial fan is characterized by a very high overall efficiency because the fan blades at the hub of the impeller have a chord length to blade height ratio in the range from about 0.5 to about 0.65, preferably about 0.57.
  • the guide vanes are advantageously curved over their height in such a way that the flow resistance is minimal.
  • the axial fan can be designed with a very high degree of efficiency with minimal flow resistance.
  • the vanes extend from an inner tube of the axial fan.
  • This inner tube is coaxial with the housing and is connected to it by the guide vanes.
  • a mounting flange for the motor is provided in the inner tube. It can be partially inserted into the inner tube and attached to the mounting flange.
  • the fan blades are designed to be twisted.
  • the fan blades can be adjusted about an axis lying transversely to the axis of rotation of the impeller. This allows the step angle of the fan blades to be adjusted to improve efficiency.
  • a further improvement in the overall efficiency is obtained in an advantageous manner if the fan blades have a ratio of chord length to blade height at their free end in the range from about 0.75 to about 0.90, preferably about 0.84.
  • the impeller has a hub ratio of about 0.2 to about 0.6, preferably about 0.45.
  • This hub ratio especially in connection with the ratios of chord length to blade height of the fan blades, contributes to the high overall efficiency of the axial fan.
  • the rear edge of the fan blades is convexly curved and the front edge is sickle-shaped.
  • the axial fans according to the Figures 1 to 4 are characterized by a high level of efficiency and a flow-optimized engine mount, which contributes significantly to the high level of efficiency.
  • the axial fan has an aerodynamically optimized impeller with a special geometry that is still to be described and a high impeller efficiency.
  • Drive motors with high motor efficiency are used for the axial fan, for example three-phase internal rotor motors or electronically commutated external rotor motors.
  • the axial fans are characterized according to the Figures 1 to 4 through flow-optimized engine mounts.
  • the axial fan according to the 1 and 2 has a motor 1, which is an internal rotor motor in the embodiment. It is attached via a suspension 2 to a cylindrical housing surrounding the motor 1 at a radial distance 3 held. It forms an outer tube of the fan and is arranged coaxially to the motor 1. How 2 1, the motor 1 is arranged so that it does not protrude axially beyond the housing 3.
  • the suspension 2 which is formed from sheet metal parts, is attached to the inside of the housing 3 and to the outside of the motor 1.
  • the suspension 2 consists of three strut parts 4 to 6 and a fastening part 8.
  • the strut parts 4 and 5 are mirror-symmetrical to one another and are each provided with a recess 7 extending over a large part of their length.
  • the strut parts 4 and 5 merge into one another in one piece via the engine-side fastening part 8 , via which the strut parts 4 , 5 are fastened to a fastening block 9 .
  • the mounting block 9 is provided on the outside of the engine 1 and has a flat bearing surface for the flat mounting part 8. In the exemplary embodiment, the mounting block 9 is spaced from an axial plane of the engine 1 running parallel to its bearing surface.
  • the mounting part 8 extends transversely to the axis of the engine 1 slightly over the mounting block 9 ( 1 ) and then transitions at an obtuse angle into the strut parts 4 , 5 having the recess 7 , the free end 11 of which is angled in such a way that it can be attached to the inner wall of the housing 3 .
  • the strut parts 4, 5 have two legs 12, 13 which lie in one plane. The legs 12, 13 run towards the free end 11 converging.
  • the recesses 7 do not extend to the ends of the strut parts 4, 5, so that the strut parts 4, 5 are solid at their ends and thus have sufficient strength in the area of attachment to the motor 1 and to the housing 3.
  • the legs 12, 13 advantageously have a width which corresponds to approximately 3 to 15 times the sheet thickness, preferably 5 times the sheet thickness. This results in optimal strength of the suspension with minimal flow resistance.
  • the support part 6 is approximately U-shaped and has two legs 14, 15 which converge in the direction of the housing 3 and which merge into one another by means of a short crosspiece 16.
  • the cross piece 16 rests against the inner wall of the housing 3 and is fastened to it in a suitable manner, for example with at least one screw 17.
  • the cross piece 16 can also be welded to the inner wall of the housing 3.
  • the free ends 18, 19 of the legs 14, 15 are angled outwards in opposite directions to one another. How out 1 shows that the free ends 18, 19 rest on the fastening part 8 of the strut parts 4, 5.
  • the attachment part 8 and the support part 6 can be attached to the attachment block 9 of the engine 1 together.
  • the attachment can be done by screws 20, but also by welding.
  • the strut parts 4 to 6 are each made of flat material, namely sheet metal parts, the sheet metal part for the strut parts 4 and 5 being bent and punched to form the recesses 7 .
  • the support part 6 is bent into the approximately U-shaped configuration described. In relation to the flow direction of the air, the sheet metal parts are arranged on edge so that they offer only little resistance to the flow.
  • the legs 14, 15 are each parallel to an axial plane of the motor 1.
  • the support part 6 is located centrally between the two strut parts 4, 5. In this way, the motor 1 is securely suspended on the housing 3.
  • the strut parts can be manufactured very easily and inexpensively from the sheet metal parts.
  • the flow resistance of the strut parts 4 to 6 can be optimally adapted to the application by selecting the size and/or design and/or position of the recesses 7 in the strut parts 4, 5.
  • the angle at which the strut parts 4 to 6 are positioned relative to one another can also be adapted to the flow conditions. In the example shown are the strut parts 4 and 6 or 5 and 6 at angles >90° to each other. Depending on the required flow resistance, this angle between the strut parts can be changed, for example 90°, less than 90° or even significantly more than 90°. Since the legs 12, 13 of the strut parts 4, 5 are arranged one behind the other in the flow direction of the air through the housing 3 and the legs 14, 15 extend with their wide dimension in the flow direction of the air, the flow resistance of the suspension 2 is minimal.
  • the strut parts 4 to 6 extend from the mounting block 9 of the engine 1 obliquely in the direction of the inlet end 21 of the housing 3.
  • the attachment points of the two strut parts 4, 5 on the housing 3 are at the same height, while the crosspiece 16 of the strut part 6 greater distance from the inlet end 21 than the free ends 11 of the strut parts 4, 5.
  • the fan blades 24 On the motor shaft 22 ( 2 ) sits non-rotatably a hub body 23, protruding from the fan blades 24. They are twisted and have a profiled cross-section. A different number of fan blades 24 is provided on the hub body 23 depending on the size of the axial fan. For example, 3 to 15 fan blades 24 can be provided, which are distributed uniformly or unevenly over the circumference of the hub body 23 . How out 2 As can be seen, the fan blades 24 have a profile 25 which is designed similar to the airfoil profile of an airplane.
  • the hub body 23 and the fan blades 24 attached to it are advantageously made of different materials. It is advantageous if the hub body 23 is an aluminum casting that can be produced inexpensively and is only light in weight.
  • the fan blades 24 are advantageously made of fiber-reinforced plastic, which also makes cost-effective production possible.
  • the fan blades 24 have a low weight and high strength. To the step angle of the fan blades 24 to be able to adjust, the fan blades 24 are pivotable on the hub body 23 in a known manner about axes lying transversely, preferably perpendicularly, to the axis of rotation of the impeller 23, 24.
  • the fan blades 24 have a concavely curved leading edge 26 and a convexly curved trailing edge 27.
  • the trailing edge 27 is designed according to the laws of bionics.
  • the trailing edge 27 can be wavy or, as in the exemplary embodiment, jagged. This profiling of the trailing edge 27 is advantageously provided over the entire length.
  • the profile 25 of the fan blade 24 is designed in such a way that the fan blade in the area of the rear edge 27 tapers out essentially to a point, while the profile 25 is rounded in the area of the front edge 26 .
  • This profile design is advantageously provided over the entire length of the fan blade 24 .
  • the fan blades 24 are provided with a cylindrical cut on their radially outer edge 28, independently of the step angle selected in each case. As a result, the edges 28 lie on a common cylinder jacket, seen in the axial direction of the fan, the axis of which is the axis of rotation of the hub body 23 . In this way, the air gap 29 between the outer edge 28 of the fan blades 24 and the inner wall of the housing 3 can be adjusted in such a way that an optimal delivery rate is achieved with minimal noise development.
  • the cylinder trimming described can be carried out by machining the impeller 23, 24 that has already been assembled, for example by milling or sawing off the fan blades 24.
  • the air gap geometry can thereby be easily and reliably optimized. In this way, the air gap 29 can be set very small, so that the flow loss is low.
  • the fan blades 24 are provided with a winglet at the outer edge 28 . They can further reduce the air flow through the air gap 29 since, together with a narrow air gap 29, they form a high resistance to the leakage flow around the outer edge 28.
  • the winglets can be created by post-processing the fan blades 24 at the outer edge 28 .
  • the fan blades 24 are machined in such a way that the respective winglet is formed at the edge 28 . This machining is carried out in such a way that a rounded transition is formed from the pressure side to the suction side of the fan blades 24 .
  • the winglets can be provided on the suction and/or on the pressure side of the fan blades 24 .
  • the motor 1 and the impeller 23, 24 are located within the cylindrical housing 3.
  • the motor 1 with the impeller 23, 24 is reliably held on the housing 3 via the suspension 2.
  • the suspension 2 offers only minimal flow resistance.
  • an axial fan results which is characterized by a high overall efficiency.
  • the hub ratio D a /D n of the impeller 23, 24 is in a range from about 0.2 to about 0.6, preferably about 0.45, contributes to the high overall efficiency.
  • D a is the outside diameter of the impeller and D n is the hub diameter.
  • the fan blades 24 have a chord length S to blade height H ratio at the hub 23 in the range of about 0.5 to about 0.65, preferably about 0.57, and a ratio in the range of about 0.75 to about 0.75 at the free end about 0.90, preferably about 0.84.
  • the fan blades 24 are formed and arranged on the hub body 23 in the same way as in the previous embodiment.
  • the fan blades 24 are advantageously connected to the hub body 23 so that they can be adjusted in order to set the step angle.
  • the fan blades 24 have the profiled trailing edge 27 and the profile 25, which is designed according to the previous embodiment.
  • the suspension of the motor 1 is formed by guide vanes 30 which are provided at an axial distance behind the impeller 23, 24 in the direction of flow of the conveyed air.
  • the guide vanes 30 are advantageously made of sheet metal, but can also be made of a correspondingly strong plastic.
  • the guide vanes 30 extend between the housing 3 and an inner tube 31 which is arranged coaxially with the housing 3 .
  • the guide vanes 30 are attached to the inside of the housing 3 and to the outside of the tube 31 in a suitable manner, for example welded or screwed.
  • the number of vanes 30 depends on the size of the axial fan. For example, 3 to 25 such guide vanes can be provided. In the illustrated embodiment, there are 7 trailing vanes 30 which form the engine mount.
  • An annular flange 32 is fastened inside the tube 31, which is designed as a flat ring disk and to which the motor 1 can be fastened.
  • the tube 31 is open at the motor-side end, so that the motor 1 can be inserted into the tube 31 for attachment to the annular flange 32 .
  • the motor 31 is advantageously provided with a counterflange which rests on the annular flange 32 and is suitably connected to it, preferably by screws.
  • the motor 1 can be, for example, a flange motor or an EC external rotor motor, on the motor shaft of which the impeller 23, 24 is fixed in a rotationally fixed manner.
  • the guide vanes 30 are advantageously continuously curved over their width.
  • the curvature is selected in such a way that good efficiency is achieved.
  • 24 results in a high overall efficiency, with the noise during operation is minimal.
  • vanes 30 are made of sheet metal, they can be manufactured in a cost-effective manner essentially by cutting and rolling.
  • the tube 31 is provided with recesses 33 distributed over its circumference at the level of the annular flange 32.
  • the impeller 23, 24 is otherwise of the same design as the impeller of the previous embodiment, so that reference can be made to the description relating to this embodiment.
  • the axial fans described can be manufactured in a wide variety of sizes.
  • the inner diameter of the housing 3 can be in a range from about 200 mm to about 1,800 mm.
  • fan blades 24 preferably consist of the plastic described, there is the possibility of using only a single injection mold for the production of the fan blades 24 for the different sizes of the fan. It is matched to the greatest length of the fan blades 24. If shorter fan blades 24 are required, they are cut to the required length. The same also applies to fan blades 24 which are made of cast metal.
  • FIG 5 shows the two strut parts 4, 5, which are connected to each other via the fastening part 8.
  • the strut parts 4, 5 each have a recess 7.
  • these recesses have no peripheral edge.
  • a supporting part 34, 35 is bent out transversely on the edge adjacent to the fastening part 8 are each provided with a recess 7'.
  • the support parts 34 , 35 and the parts of the strut parts 4 , 5 containing the recesses 7 extend at an angle to one another, so that they each enclose an angle with the planar fastening part 8 .
  • the free ends 36, 37 of the support parts 34, 35 are bent in the same direction as the free ends 11 of the strut parts 4, 5.
  • the bend 11, 36, 37 is chosen so that the strut parts 4, 5 and the support parts 34, 35 can be reliably attached to the inner wall of the housing 3 adjacent.
  • the bends have two passage openings for fastening screws or the like.
  • the bends 36, 37 can also point in a different direction than the bends 11 of the strut parts 4, 5.
  • the recesses 7 ' are also by two legs 38, 39; 40,41 converging towards the free end 36,37.
  • the recesses 7' end at a distance both from the fastening part 8 and from the free ends 36, 37.
  • the support parts 34, 35 are produced in that an approximately U-shaped stamping is made in the strut parts 4, 5 in such a way that the support parts 34, 35 fit into the in figure 5 position shown can be bent out.
  • the strut parts 4, 5, the fastening part 8 and the support parts 34, 35 are formed in one piece with one another and consist of sheet metal material.
  • simple and cost-effective production is possible.
  • Due to the additional support elements 34, 35 compared to the previous exemplary embodiments the stability of the suspension is increased considerably.
  • an even more secure attachment of the motor 1 to the housing 3 is guaranteed.
  • the strut parts 4, 5, the attachment part 8 and the support parts 34, 35 can be easily assembled and disassembled, for example by means of screws or rivets. These parts do not have to be welded, so that a costly welding process can be saved.
  • the recesses 7, 7' can be provided in such a way that the flow resistance for the air is minimal. Since the suspension consists of flat material in the manner described and has the recesses 7, 7', the suspension has only a low weight in spite of the high stability.
  • the two strut parts 4, 5 are of the same design as in the previous embodiment.
  • the fastening part 8 has, for example, a bent-out tongue 42 halfway along its length, the free end of which is provided, for example, with a passage opening for a fastening screw or the like. The free end is angled so that it can be mounted at the required location inside the axial fan.
  • the fastening part Due to the bent-out tongue 42, the fastening part has a recess 7". As in the previous exemplary embodiments, the two strut parts 4, 5 extend diverging from the fastening part 8 over the same side of the fastening part. The tongue 42 extends obliquely over the other side of the fastener 8.
  • the housing 3 can be connected via a plurality of strut parts 43 to a pot 44 in which the motor 1 is accommodated.
  • the pot 44 is cylindrical and is coaxial with the housing 3.
  • the struts 43 are of identical design and have respectively the recess 7 which is delimited by the legs 12, 13 and which converge radially outwards.
  • the radially outer and the radially inner end 11, 16 are angled in such a way that the strut parts 43 can be attached to the inner wall of the housing 3 and the outer wall of the pot 44.
  • the strut parts 43 are arranged on edge.
  • the pot 44 can also be U-shaped.
  • the strut parts 43 are attached to the mutually parallel legs 45, 46 of the pot 44.
  • the strut parts 43 are of the same design as in the embodiment according to FIG 7 . Its radially outer end 11 is fastened to the inside of the housing 3 and its radially inner end 16 is fastened to the outer sides of the legs 45, 46 of the pot 44 facing away from one another.
  • the motor 1 (not shown) is carried by the U-shaped pot 44 .
  • the pot 44 can also have an angular outline and—as in the embodiment according to FIG 7 - completely surround the engine.
  • the strut parts 43 are advantageously arranged rotationally symmetrically and/or mirror-symmetrically to one another.
  • the recess 7 can be designed such that the noise development is minimal by bevel cutting and rounding or chamfering the cut edges.
  • Figure 9a a rectangular cross-section is shown, as initially results from punching or laser cutting.
  • the cut edges are sharp and the cut faces are approximately perpendicular to the surfaces of the sheet material.
  • Figure 9b an effect similar to that in the embodiment shown in FIG Figure 9d .
  • the edge is provided with a chamfer.
  • acoustic and aerodynamic advantages are achieved in that the cut is not made perpendicular to the surface of the flat material, but at an angle to it.
  • the orientation of the cut surface can be better adapted to the direction of flow than with a cut made perpendicular to the surface of the flat material.
  • the cross sections of the legs of the strut and support parts delimiting the recesses can also be optimized in such a way that the flow resistance and the development of noise are minimal.
  • the recesses and the legs can be matched to one another in such a way that, depending on the application of the axial fan, optimally low flow resistance and noise levels can be achieved.
  • different outer diameters can be realized from essentially identical blanks by cutting the blanks to different outer diameters.
  • These blanks can be cast parts that are initially manufactured essentially identically and are adapted to the desired outside diameter in each case.
  • the fan blades 24 are to be provided with a winglet on the radially outer edge 28, then these can also be manufactured from the blanks.
  • the winglets themselves cannot yet be provided in the tool, since their geometry and their position depend on the outer diameter of the impeller and the stagger angle. It is therefore advantageous not only to cut the wing blanks with a cylinder cut, as described above, but also to give them a special contour, in particular by machining or, in the case of plastics, possibly by thermoforming can be matched to the respective stagger angle. This creates a very high level of flexibility in the design and assembly of the respective fan. Optimum acoustic properties of the blades and thus of the fan can thus be achieved for every outside diameter and stagger angle.
  • FIGS. 10a and 10d show examples of how an individual blank for the fan blade can be designed, viewed in a section approximately perpendicular to the surface of the blade suction or pressure side.
  • the blank 24 has a rectangular shape with longitudinal sides lying parallel to one another and a narrow side 47 running at right angles thereto. This shape results in particular when the design of the original wing casting tool did not include the design of a winglet.
  • a thickening or an accumulation of material 48 (winglet blank) is already provided in the wing tip area, from which the final winglet, adapted to the actual stagger angle and outer diameter, is later formed.
  • the winglet blank 48 has a rectangular cross section, but in principle it can have any desired cross section.
  • FIG. 10b and 10c two embodiments of winglets are shown schematically, which are produced by post-processing a blank accordingly Figure 10a have arisen.
  • the embodiment after Figure 10c has a straight contour of the winglet in cross section, in contrast to the embodiment Figure 10b , which has a rounded contour.
  • both winglets can be manufactured from the same wing blank. Any other shapes are also conceivable, as long as they are made from a wing blank, such as the blank here Figure 10a , are manufacturable.
  • the idea is to manufacture winglets optimally adapted to any outside diameter and with any stagger angle in a subsequent work step from a blank. It is also possible to manufacture winglets of different contours from a blank, which are optimally adapted to the respective flow conditions.
  • FIGS. 10e and 10f are, analogous to the previous description of Figures 10b and 10c , winglets shown in cross-section, made from a blank after Figure 10d were designed.
  • Fig. 10f is a fan blade with a smaller length (smaller outer diameter) but similar winglet contour as the fan blade Figure 10e implied. Both fan blades can be manufactured from the same blank.
  • the thickening 48 in the blank after Figure 10d has the advantage that there are more design options for the winglet. In order to achieve these additional design options, however, a thickening 48 is provided from the beginning in the casting tool of the wing.
  • the shape of the course of the winglet contour in the longitudinal direction of the wing can be arbitrary. It is only decisive that all winglets to be realized are geometrically within the contour of the associated blank according to the outer diameter and stagger angle to be realized. The winglets are attached in an additional work step after casting the blanks.
  • the described design of the blanks for the fan blade and the winglets is independent of whether the fans are based on the Figures 1 to 9 described suspension or have the special conditions of the fan blade geometries described.
  • the fan blades (with and without winglet) can be optimally matched to the respective fan, in particular to the respective outer diameter of the impeller and to the stagger angle, so that the optimal design of the respective fan can be easily achieved from the blanks can be.
  • the wing blanks are already provided with a winglet blank, which can then be optimally adapted to the respective application by appropriate processing.
  • the winglet shape of the blank can be arbitrary.

Landscapes

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

Claims (3)

  1. Ventilateur axial comportant un moteur (1) auquel une roue à aubes (23, 24) est fixée du côté du rotor, du moyeu (23) de laquelle des pales de ventilateur (24) dépassent en saillie, qui comportent un bord avant et un bord arrière (26, 27), et comportant une suspension (2), avec laquelle le moteur (1) est fixé à un carter (3) et présente des pièces d'entretoise (4 à 6) constituées d'un matériau plat et formées par une partie en tôle, qui raccordent le moteur (1) au carter (3) et sont disposées approximativement sur le bord dans la direction d'écoulement de l'air,
    caractérisé en ce que les pièces d'entretoise (4 à 6) sont pourvues sur une partie de leur longueur d'au moins un évidement (7) formé par un poinçonnage dans le matériau plat, que le moteur (1) et les pièces d'entretoise (4 à 6) sont disposés à l'intérieur du carter (3), que la suspension (2) se compose de trois pièces d'entretoise (4 à 6) et d'une partie de fixation (8), dont deux pièces d'entretoise (4, 5) sont configurées symétriquement l'une par rapport à l'autre et sont pourvues chacune de l'évidement (7) et se rejoignent en un seul tenant via la pièce de fixation (8) du côté du moteur, par laquelle les deux pièces d'entretoise (4, 5) sont fixées à un bloc de fixation (9) qui est prévu à l'extérieur du moteur (1) et présente une surface de contact plane pour la partie de montage (8),
    et en ce que la troisième partie d'entretoise (6) est configurée comme une pièce de support en forme de U et présente deux pans (14, 15) convergeant en direction du carter (3), qui se confondent par une courte traverse (16), qui vient en butée sur et est fixée à la paroi interne du boîtier (3) et en ce que les extrémités libres (18, 19) des pans (14, 15) sont coudées vers l'extérieur et opposées l'une à l'autre et reposent sur la partie de fixation (8).
  2. Ventilateur axial selon la revendication 1,
    caractérisé en ce que au moins une pièce de support (34, 35) dépasse d'au moins un bord de l'évidement (7), qui est avantageusement conçue en un seul tenant avec la pièce d'entretoise (4, 5).
  3. Ventilateur axial selon la revendication 1 ou 2,
    caractérisé en ce que le rapport de la largeur à l'épaisseur des pans (12, 13; 38 à 41) délimitant l'évidement (7, 7') des pièces d'entretoise (4, 5) est compris dans la plage d'environ 3 à 15, de préférence s'établit à 5.
EP13711568.9A 2012-03-06 2013-03-06 Ventilateur axial Active EP2823184B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
SI201332055T SI2823184T1 (sl) 2012-03-06 2013-03-06 Aksialni ventilator

Applications Claiming Priority (2)

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DE201210004617 DE102012004617A1 (de) 2012-03-06 2012-03-06 Axialventilator
PCT/EP2013/000649 WO2013131641A2 (fr) 2012-03-06 2013-03-06 Ventilateur axial

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EP2823184A2 EP2823184A2 (fr) 2015-01-14
EP2823184B1 true EP2823184B1 (fr) 2023-05-10

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US (1) US10781818B2 (fr)
EP (1) EP2823184B1 (fr)
JP (1) JP2015509567A (fr)
CN (1) CN104302926B (fr)
BR (1) BR112014022131B1 (fr)
DE (1) DE102012004617A1 (fr)
ES (1) ES2949380T3 (fr)
RU (1) RU2626911C2 (fr)
SI (1) SI2823184T1 (fr)
WO (1) WO2013131641A2 (fr)

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Also Published As

Publication number Publication date
ES2949380T3 (es) 2023-09-28
RU2014140100A (ru) 2016-04-27
BR112014022131B1 (pt) 2021-11-09
RU2626911C2 (ru) 2017-08-02
SI2823184T1 (sl) 2023-09-29
US10781818B2 (en) 2020-09-22
US20150023791A1 (en) 2015-01-22
EP2823184A2 (fr) 2015-01-14
CN104302926A (zh) 2015-01-21
WO2013131641A2 (fr) 2013-09-12
JP2015509567A (ja) 2015-03-30
WO2013131641A3 (fr) 2013-12-12
CN104302926B (zh) 2018-01-30
DE102012004617A1 (de) 2013-09-12
BR112014022131A2 (pt) 2017-06-20

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