EP0616132A1 - Radialgebläse, insbesondere für Gebläsebrenner - Google Patents

Radialgebläse, insbesondere für Gebläsebrenner Download PDF

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Publication number
EP0616132A1
EP0616132A1 EP94103308A EP94103308A EP0616132A1 EP 0616132 A1 EP0616132 A1 EP 0616132A1 EP 94103308 A EP94103308 A EP 94103308A EP 94103308 A EP94103308 A EP 94103308A EP 0616132 A1 EP0616132 A1 EP 0616132A1
Authority
EP
European Patent Office
Prior art keywords
impeller
housing
inlet nozzle
inlet
quadrant
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Withdrawn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
EP94103308A
Other languages
German (de)
English (en)
French (fr)
Inventor
Peter Dipl.-Ing. Bruns
Hagen Dipl.-Ing. Heuer
Ernst Dipl.-Ing. Claussen
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.)
Koerting Hannover GmbH
Original Assignee
Koerting Hannover 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 Koerting Hannover GmbH filed Critical Koerting Hannover GmbH
Publication of EP0616132A1 publication Critical patent/EP0616132A1/de
Withdrawn legal-status Critical Current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
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/4206—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps
    • F04D29/4213—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps suction ports
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23D—BURNERS
    • F23D11/00—Burners using a direct spraying action of liquid droplets or vaporised liquid into the combustion space
    • F23D11/001—Burners using a direct spraying action of liquid droplets or vaporised liquid into the combustion space spraying nozzle combined with forced draft fan in one unit
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23L—SUPPLYING AIR OR NON-COMBUSTIBLE LIQUIDS OR GASES TO COMBUSTION APPARATUS IN GENERAL ; VALVES OR DAMPERS SPECIALLY ADAPTED FOR CONTROLLING AIR SUPPLY OR DRAUGHT IN COMBUSTION APPARATUS; INDUCING DRAUGHT IN COMBUSTION APPARATUS; TOPS FOR CHIMNEYS OR VENTILATING SHAFTS; TERMINALS FOR FLUES
    • F23L5/00—Blast-producing apparatus before the fire
    • F23L5/02—Arrangements of fans or blowers

Definitions

  • the invention relates to a radial fan, in particular for forced draft burners, with an impeller rotating in a spiral housing and an axial air inlet nozzle which projects into the spiral housing at a height such that it almost bridges the existing distance between the inlet-side housing wall and the impeller front side, beginning in the first Quadrant and ending in the 2nd quadrant, the inlet-side housing wall is drawn in so far that it is approximately flush with the edge of the inlet nozzle in this area.
  • forced draft burners are equipped with a centrifugal fan that conveys the air required for combustion.
  • This fan is required to have a steep blower characteristic so that no or only slight fluctuations in volume flow occur even with larger pressure fluctuations.
  • attention must also be paid to small structural dimensions and to a low-noise mode of operation.
  • Known radial fans have a fan characteristic curve as a burner fan, ie a pressure curve as a function of the volume flow conveyed, which corresponds approximately to characteristic curve 1 in FIG. 5.
  • Burners with a flat blower characteristic curve react to this with large fluctuations in the volume flow of the combustion air, which leads to unstable combustion conditions, which are expressed in flame pulsations.
  • a steep characteristic curve leads to perfect starting behavior in terms of combustion technology.
  • Such a characteristic is also advantageous in stationary operation.
  • the flow resistance may increase due to contamination of the fan, the boiler or the chimney, or the environmental conditions, e.g. B. by climatic influences.
  • the steep characteristic curve reacts to larger fluctuations with lower volumetric flow fluctuations, which leads to very stable combustion results. Thanks to these constant combustion conditions, it is then possible to operate the burner with a lower excess of air and thereby significantly improve the efficiency of the boiler system.
  • this object is achieved with a radial blower of the generic type mentioned at the outset, the inlet nozzle of which is offset eccentrically to the impeller axis in such a way that the end of the second quadrant begins and extends into the region of the housing tongue between the impeller and the drawn-in wall of the inlet nozzle Crescent-shaped side channel is formed, which leads from the diffuser-like spiral housing into the impeller interior.
  • the impeller axis is therefore offset relative to the center of the volute casing towards the area of the casing tongue in such a way that a minimal radial gap results between the impeller and casing tongue.
  • a minimum gap is required to avoid noise.
  • At least one radially extending recess is provided in the inlet-side housing wall as a further means for sealing the high-pressure side from the low-pressure side in the region of a central angle of approximately 10 ° -50 °.
  • a vortex is formed in this depression, which prevents, or at least severely restricts, an outflow of air from the high-pressure to the low-pressure area without it participating in the pressure increase.
  • the end of the side channel located in the vicinity of the housing tongue is designed as a guide surface in such a way that the recirculating air enters the impeller interior with as little loss as possible.
  • an air guiding device protrudes into the impeller interior, which consists of an inlet surface which is bent inward and extends over the entire width of the inlet nozzle and which then, divided into two guide plates, continues, the one guide plate still is bent further inward and extends essentially in the 3rd quadrant, and the other baffle is again bent further inward, and extends essentially in the 1st quadrant. Due to this design of the air guiding device, the intake air volume flow is directed into the main delivery area of the impeller, which lies in a central angle range between 90 ° and 270 °. That which essentially extends in the 1st quadrant
  • the baffle has the special task of guiding a cross-flow vortex that forms there in the interior of the impeller to the impeller hub.
  • the radial fan according to the invention is characterized by a very steep characteristic curve and a high pressure figure. In Fig. 5 this characteristic curve is marked with 2 and shown in comparison to the characteristic curve 1 of a conventional radial fan. Due to the steep characteristic curve, the requirements outlined at the beginning are best met.
  • the radial fan according to the invention is also characterized by small dimensions and a low-noise mode of operation.
  • FIG. 2 shows a fan burner with a radial fan 1 according to the invention in section.
  • an impeller 6 driven by a motor 2. Air is sucked in via an axial inlet nozzle 3 and, compressed in the blower, is pressed into a mixing tube 5 via a mixing tube channel 4.
  • the other burner components are otherwise not shown and will not be explained further below, since they are not important for the present invention.
  • the position of the impeller 6 is indicated by dashed lines. It is wrapped spirally by the housing wall 7, which results in a diffuser-like housing extension in the radial direction.
  • the housing spiral is approximately logarithmic.
  • the impeller axis 8 is not located in the center of the housing 9, but is shifted upwards relative to this so that a minimal radial gap results between the outer circumference of the impeller 6 and the housing tongue 10, but minimizing it , but only, there are limits to noise.
  • the housing inner wall falls - as shown - from this level in one gradually widening slope 14 to the level the remaining area of the inlet-side housing inner wall.
  • the remaining, non-falling part runs out, starting at the beginning of the bevel 14, in an arcuate manner in order to connect approximately tangentially to the inner wall 15 of the inlet nozzle 3 at a central angle of 180 °.
  • the center 16 of the inlet nozzle 3 is offset with respect to the impeller axis 8 and also with respect to the housing center 9 to the 1st or 2nd quadrant, that is to say to the low-pressure side. Because of this offset, a crescent-shaped side channel 17 is created on the high pressure side, which creates a connection between the diffuser-like housing extension on the high pressure side and the impeller interior 18.
  • the inner wall 15 of the inlet nozzle 3 represents the boundary wall for the side channel 17. This begins approximately at a central angle of 180 ° and ends in the area of the housing tongue 10.
  • the end of the side channel 17 is shaped in such a way that the air recirculating through the channel is in Direction of the impeller hub is deflected.
  • the end of the side channel is designed as an oblique flat surface 19, as can also be seen from the sectional view according to FIG. 3.
  • this is designed as a curved surface 20 which is adapted to the flow.
  • other shapes are also suitable, provided they allow the recirculating air to be deflected towards the impeller hub with as little loss as possible.
  • a type of labyrinth seal 21 is provided directly behind the side channel end. This is in the range of a central angle of about 10 ° to 50 °. The seal is recessed into the housing wall on the intake side.
  • the sheet metal 13 covering the upper region of the inlet nozzle 3 is adjoined by an inlet surface 22 which is curved toward the impeller. Baffles 23, 24 which are bent inward are attached to this.
  • the gap resulting from the inwardly curved inlet surface 22 and the guide plate 23 between these and the inner edge 11 of the inlet nozzle 3 is closed by means of correspondingly adapted edge plates 26 and 25.
  • the inlet surface 22 and the guide plate 23 have the task of directing the intake air volume flow into the main delivery area of the impeller 6, which is in the range between a central angle of 90 ° and 270 °. In the first quadrant, the delivery rate is relatively small. However, there is a pronounced cross-flow vortex in the upper impeller interior, which is conducted through the guide plate 24 to the impeller hub.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
EP94103308A 1993-03-17 1994-03-04 Radialgebläse, insbesondere für Gebläsebrenner Withdrawn EP0616132A1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE9303936U 1993-03-17
DE9303936U DE9303936U1 (de) 1993-03-17 1993-03-17 Radialgebläse, insbesondere für Gebläsebrenner

Publications (1)

Publication Number Publication Date
EP0616132A1 true EP0616132A1 (de) 1994-09-21

Family

ID=6890767

Family Applications (1)

Application Number Title Priority Date Filing Date
EP94103308A Withdrawn EP0616132A1 (de) 1993-03-17 1994-03-04 Radialgebläse, insbesondere für Gebläsebrenner

Country Status (2)

Country Link
EP (1) EP0616132A1 (it)
DE (1) DE9303936U1 (it)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0972990A1 (de) * 1998-07-17 2000-01-19 MAN B & W Diesel Aktiengesellschaft Brennersystem zur nahstöchiometrischen Verbrennung von flüssigem oder gasförmigen Brennstoff
EP1002958A2 (de) * 1998-11-20 2000-05-24 PUNKER GmbH & CO. Radialgebläse
WO2008083787A1 (de) * 2006-12-28 2008-07-17 Punker Gmbh & Co. Radialgebläse und mit einem radialgebläse versehenes hochdruck-reinigungsgerät

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19501816B4 (de) * 1995-01-21 2004-11-18 Körting Hannover AG Radialgebläse, insbesondere für Gebläsebrenner
IT1288866B1 (it) * 1996-03-22 1998-09-25 F I M Fonderia Ind Meccanich E Bruciatore perfezionato per generatore di calore
FR2772437B1 (fr) * 1997-12-11 2000-02-25 Valeo Climatisation Groupe moto-ventilateur, notamment pour installation de chauffage-climatisation de vehicule automobile
DE19812561C5 (de) * 1998-03-21 2006-02-16 J. Eberspächer GmbH & Co. KG Mit Flüssigbrennstoff betriebenes Heizgerät, insbesondere für Kraftfahrzeuge

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1807385A1 (de) * 1968-11-07 1970-05-27 Punker Gmbh Appbau U Waermetec Radialventilator,insbesondere fuer OElbrenner
DE1808829A1 (de) * 1968-11-14 1970-06-04 Haase Dr Ing Dietrich Radialventilator
DE2027936A1 (de) * 1970-06-06 1971-12-16 Dr. Werner Rohrs KG, 8972 Sonthofen Ansaugführung für Radialgebläse
FR2164216A5 (it) * 1971-12-03 1973-07-27 Haase Dietrich
FR2212864A5 (it) * 1972-12-29 1974-07-26 Chauffage Automatique
WO1983002646A1 (en) * 1982-01-21 1983-08-04 Knut Olof Lennart Wallman An arrangement for radial fans
DE3238913A1 (de) * 1982-10-21 1984-04-26 Werner Dr. 8972 Sonthofen Röhrs Radialventilatorgehaeuse
DE3629132A1 (de) * 1986-08-27 1988-03-10 Buderus Heiztechnik Gmbh Geblaese fuer oel- und gasgeblaesebrenner

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1807385A1 (de) * 1968-11-07 1970-05-27 Punker Gmbh Appbau U Waermetec Radialventilator,insbesondere fuer OElbrenner
DE1808829A1 (de) * 1968-11-14 1970-06-04 Haase Dr Ing Dietrich Radialventilator
DE2027936A1 (de) * 1970-06-06 1971-12-16 Dr. Werner Rohrs KG, 8972 Sonthofen Ansaugführung für Radialgebläse
FR2164216A5 (it) * 1971-12-03 1973-07-27 Haase Dietrich
FR2212864A5 (it) * 1972-12-29 1974-07-26 Chauffage Automatique
WO1983002646A1 (en) * 1982-01-21 1983-08-04 Knut Olof Lennart Wallman An arrangement for radial fans
DE3238913A1 (de) * 1982-10-21 1984-04-26 Werner Dr. 8972 Sonthofen Röhrs Radialventilatorgehaeuse
DE3629132A1 (de) * 1986-08-27 1988-03-10 Buderus Heiztechnik Gmbh Geblaese fuer oel- und gasgeblaesebrenner

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0972990A1 (de) * 1998-07-17 2000-01-19 MAN B & W Diesel Aktiengesellschaft Brennersystem zur nahstöchiometrischen Verbrennung von flüssigem oder gasförmigen Brennstoff
EP1002958A2 (de) * 1998-11-20 2000-05-24 PUNKER GmbH & CO. Radialgebläse
EP1002958A3 (de) * 1998-11-20 2004-09-29 PUNKER GmbH & CO. Radialgebläse
WO2008083787A1 (de) * 2006-12-28 2008-07-17 Punker Gmbh & Co. Radialgebläse und mit einem radialgebläse versehenes hochdruck-reinigungsgerät
CN101652572B (zh) * 2006-12-28 2013-08-21 阿尔佛雷德·卡切尔有限责任两合公司 径流式风机以及配有一个径流式风机的高压清洁装置
US8813689B2 (en) 2006-12-28 2014-08-26 Punker Gmbh Radial fan and a high-pressure cleaning device having a radial fan

Also Published As

Publication number Publication date
DE9303936U1 (de) 1993-05-19

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