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EP0377847A1 - Ventilateur à haute pression - Google Patents

Ventilateur à haute pression Download PDF

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Publication number
EP0377847A1
EP0377847A1 EP89123080A EP89123080A EP0377847A1 EP 0377847 A1 EP0377847 A1 EP 0377847A1 EP 89123080 A EP89123080 A EP 89123080A EP 89123080 A EP89123080 A EP 89123080A EP 0377847 A1 EP0377847 A1 EP 0377847A1
Authority
EP
European Patent Office
Prior art keywords
wheel
fan
pressure
diagonal
fan wheel
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.)
Withdrawn
Application number
EP89123080A
Other languages
German (de)
English (en)
Inventor
Reinhold Hopfensperger
Rudolf Tungl
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.)
Alcatel Lucent Deutschland AG
Original Assignee
Alcatel SEL AG
Standard Elektrik Lorenz AG
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 Alcatel SEL AG, Standard Elektrik Lorenz AG filed Critical Alcatel SEL AG
Publication of EP0377847A1 publication Critical patent/EP0377847A1/fr
Withdrawn legal-status Critical Current

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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
    • F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D17/08—Centrifugal pumps
    • F04D17/16—Centrifugal pumps for displacing without appreciable compression
    • F04D17/165—Axial entry and discharge
    • 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

Definitions

  • the invention relates to a high-pressure blower, in particular a blower for gas heaters.
  • a high-pressure blower in particular a blower for gas heaters.
  • the supply and removal of combustion air in gas heaters requires fans that have a high delivery pressure and a steep pressure-volume flow characteristic, since high device resistances due to deflections, channel narrowing and other obstacles to the air flow must be overcome.
  • Fig. 9 shows pressure-volume flow characteristics of various fans.
  • Curve 1 belongs to an axial fan, curve 2 to a cross-flow fan, curve 3 to a radial fan and curve 4 to a blower according to the invention.
  • 5 is a system characteristic curve.
  • a pressure-volume flow characteristic is desired, in which larger pressure changes, for example due to changes in the system, with small ones Volume flow changes are connected. Curves 1 and 2 do not meet this condition, but curves 3 and 4 do.
  • Radial fans with drum rotors meet the above requirements and are used both on the cold side for blowing in a gas-air mixture and on the warm side for extracting the exhaust gas.
  • the required high delivery pressures in connection with the steep pressure-volume flow characteristic are either - due to narrow wheels with a large wheel diameter and narrow housing, - Or achieved by compact, compact radial radial impellers with a housing and a correspondingly high speed.
  • blowers currently used have a number of disadvantages.
  • drum rotors which are radial fans with forward-curved blades, have a lower efficiency than radial fans with rear-curved blades with the same size.
  • they are used in all applications in which high delivery pressures are important.
  • the pressure and air output of the above blowers are sensitive to the smallest changes in the housing dimensions. Therefore, only tight manufacturing tolerances are permitted in the manufacture of the housings, which means an additional cost, especially for compact designs.
  • the blowers can also be reduced in size by the available inexpensive drive motors (two-pole asynchronous machine, Shaded-pole or capacitor motor) set limits that allow speeds up to a maximum of 2800 - 2900 min ⁇ 1.
  • the object of the invention is therefore to find a blower or a fan wheel which generates high delivery pressures with a compact design and low noise emission, has a steep pressure-volume flow characteristic and avoids the disadvantages of the drum rotor.
  • This task is solved by a high pressure blower with the combination of features of the main claim.
  • the subclaims contain refinements and developments of the invention.
  • Fig. 1 shows a section through a fan wheel according to the invention. 10 with a support bell, 11 with a lid.
  • the support bell 10 is attached to a drive motor designated 12.
  • 13 denotes a medium flowing into the fan wheel
  • 14 denotes a medium flowing out of the fan wheel.
  • the gas streams can be air, air-gas mixtures or exhaust gas, depending on whether the fan wheel is used on the cold side of a gas heater or on the warm side.
  • a housing referred to which is used to forward the gas flow for gas heating or to discharge the exhaust gases.
  • 16 denotes a first region, 17 a second region and 18 a third region of the fan wheel. With 19 and 20 blades of the fan wheel are marked.
  • the blade channel cross sections of the fan wheel are large in area 16, narrow in area 17 and widen again in area 18.
  • the area 16 serves for the axial suction of the flowing medium (13) and gives the flowing medium an acceleration in the predominantly radial direction. Due to the narrowing of the blade channel cross sections in the region 17, the flowing medium is accelerated further in the radial direction, but at the same time also experiences an acceleration in the axial direction.
  • the vane channel cross sections expand like a diffuser, which leads to a conversion of speed energy into pressure energy. At the same time, the flowing medium is deflected completely in the axial direction, with energy still being transferred from the blades to the medium.
  • the fan wheel in the form shown thus represents a mixture between radial-diagonal and axial wheel.
  • FIG. 2 shows a front view of the fan wheel according to FIG. 1 with examples for the choice of the blade shape.
  • the same reference numerals designate the same elements as in FIG. 1.
  • Two types of blades are shown on the support bell 10, backward-curved blades 21 and forward-curved blades 22.
  • With 23 is an angle designated, one leg in the direction of the relative exit speed, the second leg in the direction of the peripheral speed.
  • Fig. 3 shows a second embodiment of the fan wheel according to the invention.
  • the cover and support bell are shaped differently than in the exemplary embodiment according to FIG. 1.
  • Fig. 4 shows an embodiment in which the already known fan wheel is followed by a reverse flow diagonal or semi-axial wheel 40.
  • a "diagonal wheel” for the sake of simplicity.
  • the air emerges from the diagonal wheel at the points marked 41. Since the vane channels expand like a diffuser, kinetic energy of the flowing medium is converted into static pressure energy.
  • the downstream diagonal wheel causes an improved speed distribution over the circular air outlet.
  • Fan wheel and diagonal wheel can be made in one piece, made separately and mechanically connected, or made separately and pushed onto the rotating motor or onto the motor shaft. Which of the three options mentioned is used depends on the manufacturing options and the material used.
  • an inner rotor or a motor with a rotating outer bell can be used as the drive motor 12. In the illustrated embodiments, a motor with a rotating outer bell is always used.
  • a pressure increase can be achieved not only with the help of rotating diagonal wheels, as shown in FIG. 4, but also by adding a fixed guide device.
  • 50 denotes a guide device which is connected downstream of the fan wheel driven by the drive motor 12. With 51 vane channels of the guide device are designated, which expand conically. The conical expansion of the blade channels converts the kinetic flow energy of the flowing medium into static pressure energy.
  • the guide device can be designed in such a way that its inside diameter does not change over the entire construction depth in the direction of flow (parallel to the axial direction) or is reduced (diffuser-like design of the blade channel).
  • both elements can also be connected downstream of the fan wheel.
  • FIG. 6 The fixed guide device 50 with its blade channels 51 follows the fan wheel with the support bell 10 and the cover 11.
  • a guiding diagonal wheel 40 connects to the guide device 50, from whose blade channels 41 the flowing medium flows out.
  • the sequence of guide device and diagonal wheel shown in FIG. 6 is not mandatory and can be interchanged, as shown in FIG. 7.
  • FIG. 8 shows a schematic illustration of the blade shape of the exemplary embodiment according to FIG. 6.
  • the blades of the blade 20 are shown Fan wheel to see that guide and accelerate the axially sucked medium 13.
  • the guiding device 50 is connected downstream of the fan wheel.
  • the blade shape used is designated here by 52.
  • a diagonal wheel 40 follows the guide device 50.
  • the shape of its blade is designated by 42. From Figure 8 it is clear that the flowing medium is sucked in axially, accelerated radially and finally blown off axially.
  • a further increase in pressure of the blower can be achieved in that several guide devices and diagonal wheels are connected downstream of the fan wheel.
  • guide devices and diagonal wheels are connected downstream of the fan wheel.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
EP89123080A 1988-12-19 1989-12-14 Ventilateur à haute pression Withdrawn EP0377847A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3842697 1988-12-19
DE19883842697 DE3842697A1 (de) 1988-12-19 1988-12-19 Hochdruck-geblaese

Publications (1)

Publication Number Publication Date
EP0377847A1 true EP0377847A1 (fr) 1990-07-18

Family

ID=6369518

Family Applications (1)

Application Number Title Priority Date Filing Date
EP89123080A Withdrawn EP0377847A1 (fr) 1988-12-19 1989-12-14 Ventilateur à haute pression

Country Status (2)

Country Link
EP (1) EP0377847A1 (fr)
DE (1) DE3842697A1 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0694697A1 (fr) * 1994-07-30 1996-01-31 Braun Aktiengesellschaft Roue pour une soufflante radial
NL1009755C2 (nl) * 1998-07-28 2000-02-01 Vogel Willi Ag Gascompressor.
EP1361367A2 (fr) * 2002-05-08 2003-11-12 Lg Electronics Inc. Turbosoufflante et un conditionneur d' air avec une telle soufflante
EP1423203A2 (fr) * 2001-03-05 2004-06-02 Robert Bosch Corporation Soufflante centrifuge compacte stator annulaire

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19629220B4 (de) * 1996-07-19 2005-05-12 Motoren Ventilatoren Landshut Gmbh Hochdruck-Gebläse
DE10118336B4 (de) * 2001-04-12 2016-03-24 Robert Bosch Gmbh Gebläse für eine Gas-Brennwertkesseltherme
DE102007009366B4 (de) * 2007-02-23 2017-06-14 Sew-Eurodrive Gmbh & Co Kg Lüfterrad, System und Getriebebaureihe
EP3214316B1 (fr) 2007-02-23 2019-08-07 Sew-Eurodrive GmbH & Co. KG Système et réducteur
DE102015101938A1 (de) * 2015-02-11 2016-08-11 Ebm-Papst Mulfingen Gmbh & Co. Kg Ventilatorrad und Ventilator

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH213309A (de) * 1939-10-20 1941-01-31 Wetter Wilhelm Ventilator.
US2240653A (en) * 1939-09-30 1941-05-06 Westinghouse Electric & Mfg Co Fan
DE830542C (de) * 1949-08-25 1952-02-04 Adam Elmer Dipl Ing Kreiselverdichter mit axialer Durchstroemung
DE833100C (de) * 1950-08-23 1952-03-03 Inconex Handelsgesellschaft M Turboverdichterschaufel mit Grenzschichtzaeunen
DE967862C (de) * 1944-09-18 1957-12-19 British Thomson Houston Co Ltd Diagonalverdichter mit beschaufelter Leitvorrichtung zunehmenden Querschnitts fuer gasfoermige Stroemungsmittel
GB849744A (en) * 1958-01-30 1960-09-28 Blackman Keith Ltd Improvements in fans
DE3628547A1 (de) * 1986-08-22 1988-03-03 Hans Kohl Geblaese zum foerdern von gasen

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2240653A (en) * 1939-09-30 1941-05-06 Westinghouse Electric & Mfg Co Fan
CH213309A (de) * 1939-10-20 1941-01-31 Wetter Wilhelm Ventilator.
DE967862C (de) * 1944-09-18 1957-12-19 British Thomson Houston Co Ltd Diagonalverdichter mit beschaufelter Leitvorrichtung zunehmenden Querschnitts fuer gasfoermige Stroemungsmittel
DE830542C (de) * 1949-08-25 1952-02-04 Adam Elmer Dipl Ing Kreiselverdichter mit axialer Durchstroemung
DE833100C (de) * 1950-08-23 1952-03-03 Inconex Handelsgesellschaft M Turboverdichterschaufel mit Grenzschichtzaeunen
GB849744A (en) * 1958-01-30 1960-09-28 Blackman Keith Ltd Improvements in fans
DE3628547A1 (de) * 1986-08-22 1988-03-03 Hans Kohl Geblaese zum foerdern von gasen

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0694697A1 (fr) * 1994-07-30 1996-01-31 Braun Aktiengesellschaft Roue pour une soufflante radial
NL1009755C2 (nl) * 1998-07-28 2000-02-01 Vogel Willi Ag Gascompressor.
WO2000006911A1 (fr) * 1998-07-28 2000-02-10 Willy Vogel Ag Compresseur a gaz
EP1423203A2 (fr) * 2001-03-05 2004-06-02 Robert Bosch Corporation Soufflante centrifuge compacte stator annulaire
EP1423203A4 (fr) * 2001-03-05 2005-04-20 Bosch Robert Corp Soufflante centrifuge compacte stator annulaire
EP1361367A2 (fr) * 2002-05-08 2003-11-12 Lg Electronics Inc. Turbosoufflante et un conditionneur d' air avec une telle soufflante
JP2003328991A (ja) * 2002-05-08 2003-11-19 Lg Electron Inc ターボファン及びこれを用いた空気調和機
EP1361367A3 (fr) * 2002-05-08 2004-08-18 Lg Electronics Inc. Turbosoufflante et un conditionneur d' air avec une telle soufflante
US7191613B2 (en) 2002-05-08 2007-03-20 Lg Electronics Inc. Turbo fan and air conditioner having the same applied thereto

Also Published As

Publication number Publication date
DE3842697A1 (de) 1990-06-21

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Effective date: 19910119