EP3203084A1 - Roue de ventilateur et systeme de ventilateur - Google Patents

Roue de ventilateur et systeme de ventilateur Download PDF

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Publication number
EP3203084A1
EP3203084A1 EP16153807.9A EP16153807A EP3203084A1 EP 3203084 A1 EP3203084 A1 EP 3203084A1 EP 16153807 A EP16153807 A EP 16153807A EP 3203084 A1 EP3203084 A1 EP 3203084A1
Authority
EP
European Patent Office
Prior art keywords
fan wheel
support
rotation
wheel according
support means
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
EP16153807.9A
Other languages
German (de)
English (en)
Other versions
EP3203084B1 (fr
Inventor
Matthias Wolf
Ralf Klinger
Knud Möllers
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.)
Punker GmbH
Original Assignee
Punker 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 Punker GmbH filed Critical Punker GmbH
Priority to EP16153807.9A priority Critical patent/EP3203084B1/fr
Publication of EP3203084A1 publication Critical patent/EP3203084A1/fr
Application granted granted Critical
Publication of EP3203084B1 publication Critical patent/EP3203084B1/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
    • F04D29/00—Details, component parts, or accessories
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
    • F04D29/281—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for fans or blowers
    • 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
    • F04D25/08—Units comprising pumps and their driving means the working fluid being air, e.g. for ventilation
    • F04D25/082—Units comprising pumps and their driving means the working fluid being air, e.g. for ventilation the unit having provision for cooling the motor
    • 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
    • F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
    • F04D29/281—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for fans or blowers
    • F04D29/282—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for fans or blowers the leading edge of each vane being substantially parallel to the rotation axis
    • 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
    • F04D29/58—Cooling; Heating; Diminishing heat transfer
    • F04D29/5806—Cooling the drive system
    • 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
    • F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
    • F04D29/30—Vanes

Definitions

  • the invention relates to a fan wheel for conveying a gaseous fluid, with a plurality of blades, which are arranged in a predeterminable angular pitch in an annular volume around a rotation axis and which are fixed with their axial, opposite end portions respectively to support means, wherein a first carrier means as a disk-shaped Ronde is formed coaxially to the axis of rotation and comprises a hub assembly and wherein a second carrier means is formed as a ring coaxial with the axis of rotation. Furthermore, the invention relates to a blower arrangement
  • a fan wheel may be designed as a radial fan, in particular with backward curved blades, or as a drum impeller, as for example from DE 1 628 336 A is known.
  • the Drummellaufrad consists of a large number of narrow slats, which form the blades of the wheel and which are mounted between two end rings whose radius is substantially greater than the width of the slats, so that a drum-shaped construction is formed, suitably with a Hub is connected, for example by means of a circular plate which is fixed to the slats at the center.
  • the object of the invention is a fan wheel with improved aerodynamics and improved strength properties and to provide a blower assembly with increased range of use.
  • a coaxially formed to the axis of rotation support disk is arranged, which forms an annular gap with the first support means, wherein the support disk is penetrated by at least one inlet opening, which allows a radially outwardly directed fluid flow in the annular gap.
  • a space volume of the annular gap delimited by the first carrier means and by the support disk has an axial extent along the axis of rotation which is considerably smaller than the axial extent of the annular space volume determined by the two carrier means and in which the blades are arranged are.
  • the axial extent of the annular gap along the axis of rotation is less than 20 percent, in particular less than 10 percent, of the axial extent of the annular space volume. This ensures that a fluid flow, which flows through the annular gap in the radial direction to the outside during a rotation of the fan wheel about the axis of rotation, is considerably less than a fluid flow which flows through the annular volume volume in the radial direction to the outside.
  • a mass flow of a main fluid flow through the annular space volume is at least 5 times, in particular at least 10 times, greater than the mass flow of a secondary fluid flow through the annular gap.
  • the fluid flow through the annular gap can be used for heat removal by a drive motor which is used to drive the fan wheel.
  • the support disk is connected to the hub assembly.
  • an advantageous introduction of force and torque is ensured by the hub assembly on the support disk, whereby an advantageous power flow is ensured in the fan wheel.
  • the necessary for an advantageous concentricity of the fan wheel centering of the support plate is simplified by the connection of the support disk with the hub assembly.
  • the support disk is directly connected to the first carrier means.
  • the support disk and the first support means form a stable composite, which leads to a considerable increase in the stability of the fan wheel with a suitable design of the support disk and the first support means, without requiring a considerably larger material use would be required.
  • the typically designed as a stamped sheet metal blank first carrier means is carried out in view of the connection with the support disk with a reduced material thickness and, preferably formed as stamped sheet metal blank, support plate has a material thickness which is similar to the material thickness of the first support means, in particular is identical to the material path of the first carrier.
  • the support disk and the first carrier means are materially interconnected, for example by welding, in particular reader welding, and / or gluing.
  • the projections are geometrically adapted with one of the respective opposite surface facing end face on a geometry of the opposite surface, which may be preferably flat.
  • the projections have a main extension formed in the radial direction.
  • the projections have a dual function which, in addition to the precise spacing and stable connection of the support disk and the first support means, also comprises a guiding action for the fluid flowing through the annular gap.
  • the projections are arranged on radial lines which extend from the axis of rotation in the radial direction extend to the outside.
  • the projections occupy an offset and / or an acute angle with the radial lines or at least partially curved.
  • the support disk of several, arranged in the same angular pitch to the rotation axis, in particular congruent trained, inlet openings interspersed, between which radial spokes are extended from the hub assembly to a radially outer annular region of the support disk.
  • the task of the inlet openings is to allow an axial inflow of fluid into the annular gap during a rotation of the fan wheel.
  • the inlet openings are congruent, ie geometrically congruent, and are arranged with respect to the axis of rotation in the same angular pitch to each other.
  • the inlet openings are bounded in the circumferential direction in each case by radial spokes, which are preferably web-shaped and in particular extend along radial lines which extend radially outward from the axis of rotation. Furthermore, it can be provided that the inlet openings are bounded by a radially inwardly arranged, circular-segment-shaped edge and / or by a radially outwardly arranged, circular-segment-shaped edge.
  • guide projections, in particular corrugations, of the first support means are extended along the radial spokes to the radially outer annular region, in particular up to a maximum diameter of the radially outer annular region.
  • This ensures a fluid-conducting function for the fluid flow in the annular gap.
  • the Fluid in its flow movement starting from the inlet opening, which is formed in a radially inner region of the support disk, up to the radial exit from the annular gap always out with the help of the respective guide projection in aerodynamically favorable manner.
  • support projections in particular beads, are formed, which are fixed to an opposite surface of the support disk or the first support means are.
  • These support projections serve as additional conducting means for the fluid flow in the annular gap and also contribute to the formation of a stable composite of support disk and first carrier means.
  • the support disk in a radially outer region has an at least partially circular peripheral projection which is extending in an axial direction opposite to the annular gap.
  • the task of the at least partially circular circumferential projection consists in a stabilization of the support disk.
  • a projection is formed on the blades in a radially outer region whose longest edge with the rotation axis takes an acute angle.
  • the task of this projection on the blade is to stabilize the radially outward portion of the blade, which is exposed to the largest fluid forces when using the fan wheel in a fan assembly.
  • this projection can also be used for advantageously influencing the fluid flow through the annular volume of space, wherein this fluid flow, the generation of which is the main task of the fan wheel, is considerably greater than the fluid flow through the annular gap.
  • the longest edge of the projection on the blade is aligned parallel to a connecting line between an outer edge of the first carrier designed as a disk-shaped Ronde and an inner edge of the formed as a ring second carrier means.
  • a fan assembly with a drive motor comprising a rotatably mounted on a motor housing drive shaft, and with a fan wheel according to one of the preceding claims, wherein the fan wheel with the hub assembly so fixed in rotation on the drive shaft in that the support disk is arranged adjacent to the motor housing, so that during a rotational movement of the fan wheel about the axis of rotation a fluid flow from the motor housing is effected in the direction of the support disk.
  • the fan wheel is provided to provide a main fluid flow and a secondary fluid flow during a rotation about the axis of rotation, wherein the secondary fluid flow can be used, for example, to support heat removal from the drive motor.
  • fan wheel 1 is for conveying a gaseous fluid, in particular air, provided and can be used by way of example in an oven, not shown, where it from a drive motor, not shown in FIG a rotational movement about an axis of rotation 2 is added to cause a circulation of the air volume in the oven.
  • a gaseous fluid in particular air
  • the fan wheel 1 has an example as a disc-shaped Ronde 3 coaxial with the axis of rotation 2 formed first support means and a ring 4 coaxial with the axis of rotation 2 formed second support means which are spaced along the axis of rotation 2 and arranged coaxially to each other.
  • the ring 4 is designed as a rotational body with a J-shaped profile relative to the axis of rotation 2 and forms an inlet nozzle for a main fluid flow, which is at a rotation of the fan wheel 1 about the axis of rotation 2 in the radial outward direction between the two support means 3 and 4 is encouraged.
  • the largest surface 6 extends between the blank 3 and the ring 4.
  • the largest surface 6 is flat and is arranged in a plane not shown in more detail, which is bounded by the axis of rotation 2 and a radial line 7 extending in the radial direction transversely to the axis of rotation 2.
  • a projection 8 is formed, the longest edge 9 occupies an acute angle 10 with the axis of rotation 2, as shown in the illustration of FIG. 3 is indicated.
  • each blade 5 has a lug 15, 16 aligned transversely to the largest surface 6 both on an axial end region 11 facing the blank 3 and on an axial end region 12 facing the ring 4, with which the blade 5 is fixed surface, in particular cohesively, on the blank 3 or on the ring 4.
  • the longest edge 9 of the projection 8 is aligned at least substantially parallel to a connecting line 17 between a circular outer edge 18 of the blank 3 and a circular inner edge 19 of the ring 4.
  • the blank 3 is associated with a coaxial with the axis of rotation 2 formed support disk 20 which forms an annular gap 21 with the blank 3.
  • the support disk 20 is formed as a rotational body with respect to the rotation axis 2 and provided with a plurality of inlet openings 22, which are arranged, for example, in the same angular pitch to the rotation axis 2. It can be provided that all inlet openings 22 have an identical cross-sectional geometry and are thus formed congruent.
  • the inlet openings 22 are exemplarily arranged on the support disk 20 such that radial inlets 23 are formed between the inlet openings 22, which bound the inlet openings 22 in the circumferential direction and which connect an annular inner area 24 of the support disk 20 to an annular outer area 25 of the support disk 20.
  • the inner region of the support disk is connected in a force-transmitting manner to a hub assembly 26, which in turn is connected in a force-transmitting manner to the blank 3.
  • the hub assembly 26 is exemplified as a shaft coupling, which is adapted for a rotationally fixed attachment of the fan wheel 1 on a drive shaft, not shown.
  • the Ronde 3 which may be a stamped sheet metal blank
  • several of the Supporting disk 20 facing projections 27 and 28 are formed, which are exemplified in the manner of beads realized.
  • the projections 27 are guide projections which extend in the radial direction over almost the entire diameter of the blank 3 and which are arranged in such a way that they rest on the radial spokes 23 and the adjoining outer region 25 of the support disk 20.
  • the projections 28 are formed as support projections, which rest, for example, only on the outer region 25 of the support disk 20.
  • Both the guide projections 27 and the support projections 28 have the support disk 20 facing end faces 29 which lie flat against one of the Ronde 3 facing surface 30 of the support disk 20 and there are, for example, materially bonded, in particular by gluing or welding.
  • the guide projections 27 and the support projections 28 determine the distance 31 between the blank 3 and the support disk 20 and thus also the volume of the annular gap 21.
  • the distance 31 is selected to be considerably smaller than a distance 34 between the blank 3 and the ring 4, such that upon rotation of the fan wheel 1 about the rotation axis 2, a (main) fluid flow caused by the blades 5 entering through the ring 4 in the axial direction and exiting outwardly in the radial direction between the blank 3 and the ring 4 is considerably larger than is a (secondary) fluid flow through the annular gap 21, which enters through the inlet openings 22 in the axial direction and in the radial direction outwardly between the Ronde 3 and the support disk 20 exits.
  • both the guide projections 27 and the support projections 28 are aligned with a respective main extension along radial lines, which are not illustrated in more detail, which extend starting from the axis of rotation 2 in the radial direction to the outside.
  • the support disk 20 in a radially outer region on a circular peripheral projection 32 which extends axially in a direction away from the blank 3 direction and which, as an exemplary triangular profiled bead for stabilizing the support plate 20 is provided.
  • a concave depression is formed by the projection 32 when viewing the rear side 33 of the fan wheel 1, while the surface 30 of the support disk 20 facing the disk 3, with the exception of the projection 32, is of a purely exemplary design.
  • the hub assembly 26 allows a rotationally fixed fixing of the fan wheel 1 to a drive shaft, not shown, of an engine, in particular an electric motor.
  • the fan wheel 1 is arranged on the drive shaft such that the support disk 20 faces the engine, while the ring 4 faces away from the engine.
  • a (secondary) fluid flow through the annular gap 21 can be effected, this (secondary) fluid flow, for example, heated air from the environment dissipate the engine and there helps to cool the engine.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
EP16153807.9A 2016-02-02 2016-02-02 Roue de ventilateur et systeme de ventilateur Active EP3203084B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP16153807.9A EP3203084B1 (fr) 2016-02-02 2016-02-02 Roue de ventilateur et systeme de ventilateur

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP16153807.9A EP3203084B1 (fr) 2016-02-02 2016-02-02 Roue de ventilateur et systeme de ventilateur

Publications (2)

Publication Number Publication Date
EP3203084A1 true EP3203084A1 (fr) 2017-08-09
EP3203084B1 EP3203084B1 (fr) 2020-07-15

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ID=55299323

Family Applications (1)

Application Number Title Priority Date Filing Date
EP16153807.9A Active EP3203084B1 (fr) 2016-02-02 2016-02-02 Roue de ventilateur et systeme de ventilateur

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EP (1) EP3203084B1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP4481202A1 (fr) * 2023-06-21 2024-12-25 ebm-papst Mulfingen GmbH & Co. KG Roue pour ventilateur radial

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3414188A (en) * 1966-11-25 1968-12-03 American Radiator & Standard Fan having hollow blades
DE1628336A1 (de) 1965-09-08 1970-05-21 Nordisk Ventilator Zentrifugalgeblaese mit Trommellaufrad
DE3310376A1 (de) * 1983-03-22 1984-09-27 Ebm Elektrobau Mulfingen Gmbh & Co, 7119 Mulfingen Radialgeblaese mit spiralgehaeuse
DE102008048433A1 (de) * 2008-09-23 2010-03-25 Daimler Ag Radialgebläse
EP2846046A1 (fr) * 2013-09-10 2015-03-11 Punker GmbH Roue de ventilateur

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1628336A1 (de) 1965-09-08 1970-05-21 Nordisk Ventilator Zentrifugalgeblaese mit Trommellaufrad
US3414188A (en) * 1966-11-25 1968-12-03 American Radiator & Standard Fan having hollow blades
DE3310376A1 (de) * 1983-03-22 1984-09-27 Ebm Elektrobau Mulfingen Gmbh & Co, 7119 Mulfingen Radialgeblaese mit spiralgehaeuse
DE102008048433A1 (de) * 2008-09-23 2010-03-25 Daimler Ag Radialgebläse
EP2846046A1 (fr) * 2013-09-10 2015-03-11 Punker GmbH Roue de ventilateur

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP4481202A1 (fr) * 2023-06-21 2024-12-25 ebm-papst Mulfingen GmbH & Co. KG Roue pour ventilateur radial

Also Published As

Publication number Publication date
EP3203084B1 (fr) 2020-07-15

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