EP1442223A1 - Fixation de ventilateur a compensation dynamique de desequilibre - Google Patents

Fixation de ventilateur a compensation dynamique de desequilibre

Info

Publication number
EP1442223A1
EP1442223A1 EP02762237A EP02762237A EP1442223A1 EP 1442223 A1 EP1442223 A1 EP 1442223A1 EP 02762237 A EP02762237 A EP 02762237A EP 02762237 A EP02762237 A EP 02762237A EP 1442223 A1 EP1442223 A1 EP 1442223A1
Authority
EP
European Patent Office
Prior art keywords
axial fan
fan according
hub
fan wheel
area
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
EP02762237A
Other languages
German (de)
English (en)
Other versions
EP1442223B1 (fr
Inventor
Ludger Adrian
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.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
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 Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP1442223A1 publication Critical patent/EP1442223A1/fr
Application granted granted Critical
Publication of EP1442223B1 publication Critical patent/EP1442223B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

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
    • 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
    • F04D29/662—Balancing of rotors
    • 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
    • F04D29/263—Rotors specially for elastic fluids mounting fan or blower rotors on shafts
    • 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
    • F04D29/329—Details of the hub

Definitions

  • the mass forces - static and dynamic unbalance - are caused by inhomogeneous mass distributions of the rotating assemblies rotor / anlcer and fan as well as by shape and position tolerances to the axis of rotation of the drive. Shape and position tolerances mean that the axis of rotation and the main axis of inertia no longer coincide.
  • the axial fan orients itself with increasing speed in the direction of the axis of rotation due to a soft connection of the axial fan to the armature or rotor of an electric drive.
  • the disturbance variable, i. H. the unbalance torque is automatically reduced by the rotation of the axial fan as the speed increases.
  • the influence of the shape tolerances of the axial fan wheel decreases considerably with regard to the dynamic centrifugal torque, since the axial fan wheel is self-aligned with respect to the axis of rotation.
  • the shape and position tolerances of the axial fan wheel are automatically compensated for with regard to the dynamic imbalance.
  • FIG. 1 shows an axial fan wheel, the main axis of inertia of which is tilted relative to the axis of rotation,
  • FIG. 2 shows the misalignment of the axial fan wheel on a replacement model of the axial fan wheel
  • Figure 4 shows the forces and moments acting on the replacement model of the axial fan
  • Figure 5 is a side view of an axial fan with an electric drive
  • FIG. 6 shows the top view of the hub of the axial fan wheel as shown in FIG. 5,
  • Figure 7 shows another embodiment variant of a flexible switch according to the invention
  • Figure 9 shows a fourth embodiment of a flexible coupling a
  • Figure 9.1 shows the coupling point of the axial fan wheel and drive as shown in Fig. 9 as an enlarged scale detail.
  • Fig. 1 shows an axial fan, the main axis of inertia is tilted to the axis of rotation.
  • An axial fan wheel 1 essentially comprises fan blades 2 or 3 arranged on its outer circumferential region, which are fastened to the circumference of a hub region 4.
  • An axial fan wheel 1 is preferably manufactured as a plastic injection molded component as shown in FIG. 1.
  • Such an axial fan wheel is mounted on an armature or rotor shaft of an electric drive (not shown in FIG. 1) and via the electric one Drive set in rotation.
  • the axial fan wheel 1 has a main axis of inertia, which is designated x - x in the illustration according to FIG. 1. Another axis of inertia, which is designated y-y, runs perpendicular to this.
  • a rotation axis coordinate system 8 Shifted to the aforementioned axes of inertia x -x and y - y is a rotation axis coordinate system 8, which is characterized by the rotation axis ⁇ - ⁇ and the axis ⁇ - ⁇ running perpendicular thereto. In comparison to the coordinate system spanned by the axes of inertia, the rotation coordinate system 8 is slightly tilted.
  • the axis of rotation ⁇ - ⁇ is rotatably supported in bearings, of which one bearing is designed as a fixed bearing 5, which absorbs both axial and radial forces, while the further bearing 6 is designed as a floating bearing, which can only absorb radial forces and an axial displacement of the Axis of rotation ⁇ - ⁇ of the axial fan wheel 1.
  • the reference numeral 7 denotes the center of gravity in which the axes of inertia x - x and y - y of the axial fan wheel 1 intersect, ⁇ denotes the angular velocity at which the axial fan wheel, which is driven by an electric drive (not shown here), rotates about the axis of rotation ⁇ - ⁇ .
  • the axial fan 1 is idealized as a rigid disk, while its connection area to the axis of rotation ⁇ - ⁇ is modeled as an axially acting spring arrangement 9 or 10.
  • the unbalance torque J ⁇ • ⁇ 2 is directed so that the main fan inertia axis x - x is made to coincide with the axis of rotation ⁇ - ⁇ , so that the torque supplied by the electric drive, not shown here, by the formation of the Connection of the fan modeled as a rigid disc to its hub area can be used to reduce the dynamic unbalance given by the centrifugal moment J ⁇ • ⁇ 2 .
  • the axis of rotation ⁇ - ⁇ is mounted in a fixed bearing 5 and in a floating bearing 6.
  • centrifugal torques generate considerable forces and moments depending on the speed.
  • a maximum centrifugal torque of 45000 gmm 2 for example, the axial fan wheel 1 has an unbalance torque of 2500 rpm
  • the moment acts in the direction of the arrow on an axis of the axial fan wheel, which is modeled as a rigid disk and extends perpendicular to the plane of the drawing.
  • the axial fan wheel 1 is displaced by the angle ⁇ into the position denoted by ⁇ - ⁇ , also denoted by reference symbol 1 '.
  • the main axis of inertia x -x of the axial fan wheel 1 approaches the position of the axis of rotation ⁇ - ⁇ about which the axial fan wheel 1 rotates at the angular velocity ⁇ .
  • Fig. 4 shows the forces and moments acting on the replacement model of the axial fan.
  • ⁇ minus denotes the misalignment of the axial fan wheel 1 modeled as a rigid disk 1 at a given speed ⁇ ⁇ 0.
  • the centrifugal torque J ⁇ • ⁇ 2 is used as the speed increases due to the soft connection of the hub area 5 to the rotation axis ⁇ - ⁇ .
  • the axial fan wheel 1 which is modeled as a rigid disk in the illustration according to FIG.
  • the torque relationship for the axial fan wheel 1 that occurs with respect to the axial fan wheel 1 is:
  • the axial fan wheel 1 orients itself during its rotation about the axis of rotation ⁇ - ⁇ such that the axis of rotation ⁇ - ⁇ and the main axis of inertia x -x of the axial fan wheel 1 coincide.
  • the axial or radial forces which are established on the bearings 5 and 6 of the axis of rotation ⁇ - ⁇ by axial fan wheel 1 are identified in the illustration according to FIG. 4 by the reference numerals 11, 12 and 13.
  • FIG. 5 shows the side view of an axial fan with an electric drive.
  • the axial fan wheel 1 comprises in its outer circumferential area a number of fan blades 2 or 3 which are formed on the circumference of a hub area 4.
  • the axial fan wheel 1 is connected to an output shaft 20 of an electric drive 21.
  • the electric drive 21 is accommodated in a housing 22 which partially projects into the cup-shaped hub area 4 of the axial fan wheel 1 in order to shorten the axial overall length of the fan arrangement as shown in FIG. 5.
  • a disk 23 made of flexible, elastic material can be accommodated, which is connected to a plate-shaped or cup-shaped area 27 of the hub area 4 of the axial fan wheel 1.
  • Fastening screws 24 are used to connect the elastic disk 23 received on the output shaft 20 of the electric drive 21 to the cup-shaped hub plate 27 of the hub area 4.
  • the fastening screws 24 can be used to increase the flexibility of the connection between the elastic disk 23 and the hub plate 27 in the hub area 4 of the axial fan wheel 1 be equipped with spring elements 30.
  • the fairy- the elements 30 can be provided on the fastening screws 24 either in the area of the cup-shaped recessed hub plate 27 or between the fastening screws 24 and the elastic disk 23.
  • Reference numerals 25 denote holders with which the housing 22 of the electric drive 21 can be attached to a radiator assembly in the engine compartment of a motor vehicle.
  • Designated by 26 is a balancing weight which is received for the static balancing of the axial fan impeller 1 on a fan blade 3 on the circumference of the hub area 4 of the axial fan impeller 1 as shown in FIG. 5.
  • hub or disk bores 28 are formed in these two components, which are penetrated by the fastening screws 24 with spring elements 30 optionally held thereon.
  • the hub bores 28 are arranged on a hub bore pitch circle 29, which is shown in more detail in FIG. 6.
  • FIG. 6 shows the top view of the hub of the axial fan wheel according to FIG. 5.
  • the cup-shaped hub area 4 of the axial fan wheel according to the illustration in FIG. 5 here comprises slots 31 extending 120 ° on the circumference of the hub area offset from one another in the radial direction.
  • the slots 31 have a length 32 which corresponds to the respective slot width 33 many times.
  • the hub area 4 of an axial fan wheel 1 can also be formed with 4, 5, 6 or an even higher number of radial slots 31.
  • the hub bores 28 already mentioned in connection with FIG. 5 can be formed in the hub area 4 on a screw pitch circle diameter 29, the diameter of which is less than half the diameter of the hub area 4 Axial fan wheel 1. The further the hub bores 28, of which only three are arranged on the screw pitch circle diameter 29 in the illustration according to FIG.
  • a further possibility of achieving a flexible connection of the hub area 4 with the output shaft 20 of an electric drive 21 is to reduce the material thickness in the hub area 4 in the area of the hub plate 27 which is inserted like a cup. Furthermore, a more flexible connection of the hub area 4 to the output shaft 20 of the electric drive 21 can be achieved in that on the spring elements 24, which connect the elastic disk 23 and the cup-shaped hub plate 27 of the hub area 4 to each other, spring elements are formed which, depending on the deflection, generate spring moments F c • a which increase with increasing Counteract increasing centrifugal torque J ⁇ .
  • the axial fan wheel 1 is oriented such that its main axis of inertia x - x coincides with the axis of rotation ⁇ - ⁇ and no vibrations can be transmitted through structure-borne noise to other structural components in the engine compartment of a motor vehicle or to the interior of a motor vehicle.
  • FIG. 7 shows a further embodiment variant according to the invention of a flexible mounting of an axial fan wheel on a drive.
  • an elastic driver 23 and a hub plate 27 of the axial fan wheel 1 connected to the elastic driver 23 are accommodated on the armature shaft 20 of an electric drive (not shown here).
  • the elastic driver 23 is provided with an S-shaped configuration 50, which extends on the elastic driver 23 in its radial direction.
  • the hub plate 27 of the axial fan wheel 1 is screwed in the area of the screw connection circle 29 by means of fastening screws 24 to screw-in threads of the elastic driver 23.
  • a spacer bushing 37 is accommodated between the screw heads of the fastening screws 24 and the plane end face of the driver 23 made of elastic material. This rests with a contact surface 39 on the flat end face of the driver 23 made of elastic material.
  • a circumferential recess 35 is received on the hub plate 27, into which an elastic element is embedded.
  • the elastic element 36 can be accommodated, for example, as shown in FIG. 7 as an O-ring which surrounds the spacer bush 37. In its undeformed, ie unloaded state, If the O-ring embedded in the circumferential recess 35 shows a deflection s, which is identified in the illustration according to FIG. 7 with reference symbol 38. This means that the hub plate 27 of the axial fan wheel can move by the tilting angle ⁇ shown in FIG. 7, by virtue of the fact that insert element 36 let into the recess 35 creates a flexible connection between the elastic driver 23 and the hub plate 27 of the axial fan wheel 1.
  • FIG. 8 shows a third embodiment variant of a flexible coupling of an axial fan wheel to a drive.
  • FIG. 8 also shows a driver 23 made of elastic material with an S-shaped profile 50 and a hub plate 27 connected to it by means of fastening screws 24.
  • a corrugated disk 40 made of metallic material is embedded in the circumferential recess 35 on the hub plate 27 of the axial fan wheel.
  • the corrugated washer 40 made of metallic material and embedded in the circumferential recess 35 also enables a flexible coupling of the hub plate 27 of the axial fan wheel 1 to the driver 23 made of elastic material. It can be seen from the illustration in FIG.
  • a deflection path s is set by the corrugated disk 40 shown in the rest state between the flat surfaces of the hub plate 27 and the elastic driver 23, which in the illustration according to FIG. 8 is analogous to the illustration according to FIG ..7 is denoted by reference 38.
  • the deflection s ensures that the hub plate 27 with the axial fan wheel 1 formed thereon can move by the angle ⁇ , so that a relative movement of the hub plate 27 to the elastic driver 23 received on the armature shaft 20 is ensured.
  • the fastening screws 24, with which the hub plate 27 of the axial fan wheel 1 is connected to the face-end face of the elastic driver 23, are arranged in the screw pitch circle 29.
  • FIG 9 shows a fourth embodiment of a flexible coupling of an axial fan wheel to the drive with a deflection area.
  • the axial fan wheel 1 as shown in FIG. 9 is received on the armature shaft 20 of an electric drive 21 with the interposition of a bushing element 42.
  • the electric drive 21 is installed on a structural element of a vehicle via a holder 25, shown schematically here.
  • the axial fan wheel 1 comprises fan blades 2, in which balancing weights 26 can be arranged.
  • the holders 25 are arranged, for example, at an angle of 120 ° to one another.
  • the hub plate 27 of the axial fan wheel 1 encloses the electric drive 21 partially.
  • the area designated by the letter Y in FIG. 9 is reproduced in the illustration according to FIG. 9.1 as a detail enlarged on a scale.
  • a bushing element 42 is accommodated in the area of a seat surface 46 of the connector shaft 20 of the electric drive 21.
  • the bushing element 42 is pressed against a bearing ring 47 by means of a tensioning element 43, which is also supported on the shaft 20 in the area of an annular groove 45.
  • the bearing ring 47 completely surrounds the armature shaft 20 of the electric drive 21.
  • the tensioning element 43 which can be configured, for example, as a tensioning disk, is supported with one leg on a flank of an annular groove 45 introduced into the armature shaft 20, while the leg of the tensioning element 43, which extends further outwards, is supported on the through the bushing element 42 and Hub plate 27 of the axial fan 1 supports the end face.
  • the hub plate 27 and the socket element 42 are connected to one another via fastening screws 24.
  • the clamping element 43 By means of the clamping element 43, the bushing element 42, which has a support 44, is placed in the axial direction against a contact surface 49 on the contact ring 47. As a result, the socket element 42 is fixed in the axial direction.
  • the armature shaft 20 of the electric drive 21 has a seat 46 on which the support 44 of the socket element 42 rests.
  • the support 44 represents a tilting point of the bushing element 42 secured on the anlcer shaft 20 in the axial direction and of the bushing element 42 which can be tilted in the radial direction.
  • a relative movement of the bushing element 42 to the seat surface 46 of the angling shaft 20 can cause an inclined position of the take place on the tiltably mounted bushing element 42 of the hub plate 24 and thus the axial fan wheel 1.
  • Dynamic unbalances that occur are automatically compensated for by this mounting of the bushing element 42, acted upon by a tensioning element 43 during the rotation of the anchor shaft 20 of the electric drive 21.
  • the required tilt angle can be calculated from the expected dynamic unbalance of the fan. This is briefly explained using a sample calculation. With a blower with 25000 gmm 2 expected dynamic unbalance, the required soft tilt angle can be determined from the relationship
  • the design path s marked with reference numeral 38 amounts to approximately 3/10 mm for the given example based on the given data.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • External Artificial Organs (AREA)
  • Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)
EP02762237A 2001-10-30 2002-08-06 Fixation de ventilateur a compensation dynamique de desequilibre Expired - Lifetime EP1442223B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10153412A DE10153412A1 (de) 2001-10-30 2001-10-30 Lüfterbefestigung mit dynamischem Unwuchtausgleich
DE10153412 2001-10-30
PCT/DE2002/002881 WO2003040570A1 (fr) 2001-10-30 2002-08-06 Fixation de ventilateur a compensation dynamique de desequilibre

Publications (2)

Publication Number Publication Date
EP1442223A1 true EP1442223A1 (fr) 2004-08-04
EP1442223B1 EP1442223B1 (fr) 2009-01-21

Family

ID=7704136

Family Applications (1)

Application Number Title Priority Date Filing Date
EP02762237A Expired - Lifetime EP1442223B1 (fr) 2001-10-30 2002-08-06 Fixation de ventilateur a compensation dynamique de desequilibre

Country Status (7)

Country Link
US (1) US6908284B2 (fr)
EP (1) EP1442223B1 (fr)
JP (1) JP2005509109A (fr)
KR (1) KR100944648B1 (fr)
AT (1) ATE421639T1 (fr)
DE (2) DE10153412A1 (fr)
WO (1) WO2003040570A1 (fr)

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CN102939701B (zh) * 2010-06-14 2015-05-06 松下电器产业株式会社 风扇马达、使用了该风扇马达的车载用空调装置以及风扇马达的组装方法
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Also Published As

Publication number Publication date
WO2003040570A1 (fr) 2003-05-15
KR100944648B1 (ko) 2010-03-04
EP1442223B1 (fr) 2009-01-21
DE10153412A1 (de) 2003-05-15
US20040013517A1 (en) 2004-01-22
ATE421639T1 (de) 2009-02-15
DE50213244D1 (de) 2009-03-12
US6908284B2 (en) 2005-06-21
KR20040047985A (ko) 2004-06-05
JP2005509109A (ja) 2005-04-07

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