EP0589300B1 - Radialgebläse - Google Patents

Radialgebläse Download PDF

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Publication number
EP0589300B1
EP0589300B1 EP93114532A EP93114532A EP0589300B1 EP 0589300 B1 EP0589300 B1 EP 0589300B1 EP 93114532 A EP93114532 A EP 93114532A EP 93114532 A EP93114532 A EP 93114532A EP 0589300 B1 EP0589300 B1 EP 0589300B1
Authority
EP
European Patent Office
Prior art keywords
rotor wheel
impeller
suction space
radial blower
housing
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.)
Expired - Lifetime
Application number
EP93114532A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0589300A1 (de
Inventor
Siegfried W. Schilling
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
Individual
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
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Application filed by Individual filed Critical Individual
Publication of EP0589300A1 publication Critical patent/EP0589300A1/de
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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
    • F04D29/08—Sealings
    • F04D29/16—Sealings between pressure and suction sides
    • F04D29/161—Sealings between pressure and suction sides especially adapted for elastic fluid pumps
    • F04D29/162—Sealings between pressure and suction sides especially adapted for elastic fluid pumps of a centrifugal flow wheel
    • 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
    • F04D17/02—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps having non-centrifugal stages, e.g. centripetal
    • F04D17/04—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps having non-centrifugal stages, e.g. centripetal of transverse-flow type
    • 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
    • F04D25/16—Combinations of two or more pumps ; Producing two or more separate gas flows
    • F04D25/166—Combinations of two or more pumps ; Producing two or more separate gas flows using 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
    • F04D29/40—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

Definitions

  • the invention relates to a radial fan according to the preamble of claim 1 as is known for example from DE-A-2 540 580.
  • Radial fans in particular with an impeller designed as a drum rotor, are used on a large scale because of their simple construction. In particular, such radial fans are also used for conveying combustion air in oil and gas burners. Simple radial fans, however, operate in an air-volume range which is unfavorable for use with such burners and in which pressure instabilities occur. Modern oil and gas burners, however, require fans with relatively high static pressures and stable, steep P / V characteristics to ensure stable operation.
  • Known radial blowers for example DE-OS 23 62 815) therefore have an annular gap between the wheel cover plate of the impeller and the cover plate merging into the axial inflow opening. A part of the compressed air flows through this annular gap from the pressure chamber of the one surrounding the impeller Housing in the suction chamber inside the impeller and flows through the impeller again radially, so to speak to be compressed in a second stage.
  • a radial blower of the type mentioned at the outset projects into the interior of the impeller Partition provided.
  • the partition divides the interior into a first suction chamber, in which the inflow opening opens and the fresh air is sucked in, and into a second suction chamber, in which only air flows back from the pressure chamber of the housing via the annular gap.
  • the second suction chamber thus essentially serves to compress the air flowing back out of the housing via the annular gap. The air flowing back into the second suction space does not mix with the fresh air flowing into the first suction space, so that the post-compression becomes more effective and higher static pressures are achieved.
  • a radial fan is known from DE-A-1 808 829 and FR-A-2 164 216, in which the impeller is arranged between two cover plates of the housing, which are designed as plane-parallel disks. An axial gap remains between the impeller and the disks, which enables undesirable pressure equalization even with a small width.
  • a partition projects into the interior of the impeller and divides the interior into a first and a second suction space. An inflow opening opens into the first suction chamber. The partition is arranged so that it connects to the tongue edge of the housing.
  • the part of the impeller which is separated by the partition and has the first suction space works as a radial fan, while the other part of the impeller works as a cross-flow fan which conveys the air ejected by the part of the impeller working as a radial fan to the outlet of the housing.
  • the invention is based on the problem of creating a radial blower which is further improved with regard to the static pressures which can be achieved and the P / V characteristic.
  • the annular gap forms a continuous connection of the housing in front of the axial end face of the impeller, via which the outlet-side end of the housing is "short-circuited" with high static pressure with the initial region of the housing with lower pressure.
  • the invention is based on the idea of closing the axial end face of the impeller against the housing and thus the pressure side and sealing it as far as possible. This prevents air from passing from the high pressure side to the low pressure side of the housing past the impeller and the disadvantageous pressure equalization is minimized.
  • the impeller works as a cross-flow blower, which sucks air from the outlet-side area of the housing with high static pressure into the second suction space and conveys it into the initial area of the housing with low static pressure.
  • the radial fan thus works as a two-stage fan with a first stage acting as a radial fan and a second stage as a cross-flow fan.
  • the tight sealing of the axial end face of the impeller is achieved in a structurally particularly simple manner in that the cover plates are formed by two fixed plane-parallel disks.
  • the clear distance between the two disks is at the same time the clear width of the radial outlet cross section of the impeller.
  • the two disks can merge into the housing enclosing the impeller on its circumference and in particular can be an integral part of the housing wall. This results in an inexpensive manufacture and assembly, so that this version is particularly suitable for the production of large quantities.
  • the impeller with the two discs forms an independent installation module that can be used in different housings.
  • the built-in module can be inexpensively manufactured in large numbers, while the adaptation to the different burner types is ensured by the use of different housings.
  • the impeller Since the discs covering the front of the impeller are fixed and the impeller rotates, a minimal gap between the impeller and the discs is inevitable.
  • the impeller is preferably immersed in recesses in the surface of the disks, so that a labyrinth sealing system is formed between the rotating impeller and the fixed disks.
  • the sealing effect of this labyrinth sealing system can be further improved in that the wheel support disk and the wheel cover disk have an outwardly projecting collar on their outer circumference which runs in a groove pierced into the respective disk.
  • the partition dividing the interior of the impeller is expediently formed on the cover plate that closes the end face.
  • the partition wall is guided axially as close as possible to the wheel support disk of the impeller and laterally to close to the inner contour of the blading.
  • An inclination of the partition against the plane of the wheel support plate favors the intake flow and, if necessary in conjunction with a flank angle of the axial side edges of the partition, reduces the noise formation in relation to the surface line of the blading.
  • the passage cross section of the inflow opening is significantly smaller than the cross section of the first suction chamber and if the volume of the second suction chamber is greater than the volume of the first suction chamber.
  • the housing is designed with a diffuser.
  • the tongue edge of the housing is in the angular range of the second suction chamber, which acts as a cross-flow fan.
  • the housing is designed with two diffusers.
  • the part of the impeller acting as a radial fan sucks the air into the first suction chamber and blows it into the initial area of the first diffuser, which serves as the pressure chamber of the radial fan.
  • the widened end region of the first diffuser lies in the peripheral region of the cross-flow fan part and is separated from the second diffuser by a second tongue edge, which serves as a pressure chamber of the cross-flow fan and leads to the outlet of the housing.
  • the partition is fixed in its angular position.
  • the partition wall adjustable in its angular position with respect to the tongue edge of the housing, whereby in particular the area ratio of the inlet and outlet sections of the crossflow fan separated by the tongue edge can be changed and the compression of the crossflow fan stage can be adjusted.
  • 1 and 2 show a first embodiment of the radial fan.
  • the radial fan is flanged to a motor 12 indicated by dash-dotted lines and is driven by its shaft 14.
  • the radial fan has an impeller 16 designed as a drum rotor, which consists of a wheel support disk 18 seated on the motor shaft 14, a blading 20 fastened to the wheel support disk 18 and an annular wheel cover disk 22 holding the free ends of the blading 20.
  • the impeller 16 is thus a conventionally constructed drum rotor, the blading 20 of which has an exit angle greater than 90 °, i.e. the blading 20 is directed in the direction of rotation of the impeller 16 shown by an arrow in FIG.
  • the ratio of inside diameter to outside diameter of the blading is 0.7 to 0.85.
  • the impeller 16 is enclosed on its outer circumference by a housing 24, which is guided with a tongue edge 26 along a surface line to the outer circumference of the impeller 16 and expands in the direction of rotation of the impeller 16 as a diffuser to an outlet 28.
  • the axial end faces of the housing 24 are formed by cover plates which have the shape of plane-parallel disks 30 and 32.
  • the first disc 30 is flanged to the motor 12 and is by the Wave 14 penetrates.
  • the second disk 32 has an annular recess 36 into which the end of the blading 20 with the wheel cover disk 22 is immersed.
  • labyrinth sealing systems By immersing the impeller 16 with the wheel support disk 18 into the recess 34 and the blading 20 with the wheel cover disk 22 into the recess 36, labyrinth sealing systems each result on the axial end faces of the impeller 16. These labyrinth sealing systems prevent pressure losses due to pressure equalization from the high pressure side of the housing 24 at the outlet 28 to the low pressure side of the housing 24 behind the tongue edge 26 via the gap between the wheel support plate 18 and the first plate 30 and via the gap between the wheel cover plate 22 and the second disc 32.
  • the labyrinth sealing system prevents air from the housing 24, ie from the pressure side of the radial fan, axially through the gap between the impeller 16 or its wheel cover plate 22 and the second plate 32 flows axially into the interior of the impeller 16.
  • the sealing effect of the labyrinth sealing systems is further improved in that the wheel support plate 18 and the wheel cover plate 22 each have an axially flared collar 38 on their outer circumference, each of which plunges into a circular groove 40 pierced into the plane of the disk 30 or 32.
  • a partition 42 is arranged, preferably integrally formed, on the second disk 32 that closes the open axial end face of the impeller 16.
  • the partition 42 protrudes axially from the second disc 32 into the impeller 16 and extends with its free end edge as close as possible to the wheel support disc 18.
  • the gap S remaining between the end edge of the partition 42 and the wheel support disc 18 is between 0.2 and 4 by design mm.
  • the partition 42 adjoins the inner circumferential surface of the impeller 16. The partition 42 thus divides the interior of the impeller 16 as tightly as possible into a first suction chamber V1 and a second suction chamber V2.
  • the partition 42 extends transversely, substantially at right angles to the axial plane extending through the axis of the impeller 16 and the tongue edge 26.
  • the partition 42 is arranged eccentrically to the axis of the impeller 16 and divides the inner diameter of the impeller 16 perpendicular to the partition 42 in a ratio H1: H2 of 0.65 to 1.0.
  • the larger diameter section H2 corresponds to the second suction chamber V2 facing the tongue edge 26.
  • the partition 42 runs parallel to the axis of the impeller 16.
  • the partition 42 is at an angle Winkel of up to 30 °, preferably approximately 15 °, with respect to the axial plane slanted, the free end edge of the partition 42 the larger Has distance from the axis of the impeller 16.
  • the axial side edges of the partition wall 42 have a flank angle of up to 15 °, preferably of about 5 °, so that the width of the partition wall 42 tapers towards its free end.
  • the inclination of the partition 42 in the embodiment of Figure 3 has the result that when the impeller 16 rotates the inner edges of the blades 20 do not simultaneously overlap with the side edges of the partition 42 over the entire axial width, but these side edges only in one intersect axially moving point. This reduces the running noise of the radial fan.
  • the second suction chamber V2 is completely covered by the second disk 32, so that it is largely airtight on its two axial end faces.
  • the second disc 32 has an inflow opening 44 through which fresh air can be sucked into the first suction chamber V1.
  • the inflow opening 44 preferably has a circular cross section, its area being substantially smaller than the end face of the first suction space V1.
  • the inflow opening 44 is arranged approximately centrally in relation to the end face of the first suction space V1.
  • the fresh air sucked in when the impeller 16 rotates through the inflow opening 44 is set in the first suction space V1 by the blading 20 into a vortex rotation parallel to the impeller 16.
  • the blades 20 of the rotating impeller 16 take this vortex with it in the direction of rotation, so that this vortex tends to migrate away from the inflow opening 44 in the direction of rotation.
  • This effect is caused by a guide bead 46 counteracted, which is integrally formed on the inner surface of the second disc 32 and adjoins the inflow opening 44 in the direction of rotation of the impeller 16.
  • the approximately triangular guide bead 46 has an axial height which is approximately 0.25 to 0.5 times the axial width B1 of the blading 20.
  • the guide bead 46 prevents the vortex of the incoming fresh air from migrating and holds this vortex at the inflow opening 44. In conjunction with the relatively small cross section of the inflow opening 44, this results in a high suction power of the impeller 16 in the region of the first suction space V1.
  • the impeller 16 When the impeller 16 rotates in the direction of the arrow, the impeller 16 acts as a radial fan in the region of the first suction chamber V1. Fresh air is sucked axially into the first suction chamber V1 through the inflow opening 44 and accelerated radially outward into the housing 24 through the blading 20 over the circumferential region of the first suction chamber V1. In the expanding diffuser of the housing 24, a static pressure builds up against the outlet 28.
  • the impeller 16 In the area of the second suction chamber V2, the impeller 16 is sealed off on its two axial end faces, in the interior the partition 42 forms a tight seal and on the outer circumference opposite the partition 42, the tongue edge 26 seals the impeller 16.
  • the impeller 16 therefore works in the area of the second suction space V2 exclusively as a cross-flow fan, which draws in the air from the pressure space in the area of the outlet 28 and ejects it in the initial area of the diffuser of the housing 24 behind the tongue edge 26.
  • the radial blower thus works as a two-stage blower with a first stage formed by the first suction chamber V1 as a radial blower and a second stage formed by the second suction chamber V2 as a cross-flow blower.
  • the disks 30 and 32 are guided beyond the circumference of the impeller 16 and also form the axial cover plates of the housing 24 in one piece. This enables the entire housing 24 including the disks 30 and 32 to be produced inexpensively from two one-piece injection molded parts. This version is particularly suitable if the blower is manufactured in large numbers.
  • FIGS. 4 and 5 show a further modification which enables the radial fan to be adapted to different mounting configurations.
  • the disks 30 and 32 and the impeller 16 correspond to the designs described above in connection with FIGS. 1 and 2 and 3, respectively, so that reference can be made to the previous description in this respect.
  • the disks 30 and 32 are not formed in one piece with the cover plates of the housing, but only protrude with an edge 48 over the outer circumference of the impeller 16.
  • the disks 30 and 32 are through some Holding pins 50 distributed over the circumference are connected to one another.
  • Guide blades 52 are placed on the holding pins 50 and serve as spacers between the disks 30 and 32.
  • the guide blades 52 are curved in the sense of the blading 20 of the impeller 16, so that they do not impair the flow behavior of the impeller.
  • the impeller 16 with the disks 30 and 32 is mounted to the complete self-supporting built-in module by means of the holding pins 50.
  • This built-in module can be inserted into a corresponding recess in a housing 24 corresponding to the respective requirements and is fastened in the housing, for which purpose, for example, a radially projecting flange 54 of the first disk 30 is used, which has bores 56 for screwing to the housing 24.
  • FIG. 6 shows a fourth embodiment in which the impeller 16 and the disks 30 and 32 receiving and closing the impeller 16 are also formed in one of the embodiments described above.
  • the housing has two diffusers which adjoin one another in the circumferential direction and are each separated from one another by a tongue edge leading to the circumference of the impeller 16.
  • a first tongue edge 58 lies in the area of the partition 42 on the outer circumference of the impeller 16, so that a first pressure chamber 60 is formed which extends along the first suction chamber V1 and extends into the peripheral region of the second suction chamber V2 and approximately in the middle of the peripheral region of the second suction chamber V2 is closed off by a second tongue edge 62.
  • a second pressure chamber 64 widens in the circumferential direction from the second tongue edge 62 to the outlet 28.
  • the operation of the radial fan of this embodiment corresponds essentially to the operation described above.
  • Fresh air is drawn through the inflow opening 44 into the first suction chamber V1 and is conveyed radially into the first pressure chamber 60.
  • the first pressure chamber 60 thus serves as the pressure chamber of the part of the impeller 16 working as a radial fan with the first suction chamber V1.
  • the air compressed by this radial fan stage in the first pressure chamber 60 then flows through the impeller 16 in the region of the second suction chamber V2 and is conveyed to the second pressure chamber 64 in a compressed manner.
  • the part of the impeller 16 with the second suction chamber V2 also acts here as a second post-compression fan stage, which works as a cross-flow fan.
  • the partition wall 42 is arranged essentially at right angles to the axial plane which runs through the axis of the impeller 16 and the tongue edge 26 or 62 associated with the second suction chamber V2.
  • the inlet cross section and the outlet cross section are those that act as cross-flow fans second suction chamber V2 essentially the same. If the partition 42 is arranged rotated at an angle with respect to the arrangement shown, so that the inlet cross section of the second suction space V2 increases and its outlet cross section decreases, there is a greater pressure increase by the cross-flow fan.
  • the achievable static pressure can thus be influenced by the angular position of the partition wall 42. It is also possible to fix the second disc 32 with the partition 42 so as to be adjustable in angle in order to enable the static pressure to be set individually.
  • FIG. 7 shows a P / V diagram of the static pressures which can be achieved as a function of the conveyed air volume flow.
  • the characteristic curve of the radial fan according to the invention is designated by I and compared with the characteristic curve of a conventional radial fan designated by II. It can be seen that up to a factor of 4 higher static pressures can be achieved with the radial fan according to the invention.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Toys (AREA)
  • Massaging Devices (AREA)
EP93114532A 1992-09-25 1993-09-10 Radialgebläse Expired - Lifetime EP0589300B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4232178A DE4232178C1 (de) 1992-09-25 1992-09-25 Radialgebläse
DE4232178 1992-09-25

Publications (2)

Publication Number Publication Date
EP0589300A1 EP0589300A1 (de) 1994-03-30
EP0589300B1 true EP0589300B1 (de) 1996-12-11

Family

ID=6468849

Family Applications (1)

Application Number Title Priority Date Filing Date
EP93114532A Expired - Lifetime EP0589300B1 (de) 1992-09-25 1993-09-10 Radialgebläse

Country Status (4)

Country Link
EP (1) EP0589300B1 (da)
AT (1) ATE146259T1 (da)
DE (3) DE4232178C1 (da)
DK (1) DK0589300T3 (da)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1002957A2 (de) * 1998-11-20 2000-05-24 PUNKER GmbH & CO. Radialgebläse
EP1002958A2 (de) * 1998-11-20 2000-05-24 PUNKER GmbH & CO. Radialgebläse
EP1022469A1 (de) 1999-01-20 2000-07-26 PUNKER GmbH & CO. Radialgebläse
EP1022470A1 (de) 1999-01-20 2000-07-26 PUNKER GmbH & CO. Radialgebläse
US6604906B2 (en) 2000-08-04 2003-08-12 Calsonic Kansei Corporation Centrifugal multiblade blower

Families Citing this family (11)

* 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
DE19832132C1 (de) * 1998-07-17 1999-12-16 Man B & W Diesel Ag Brenner zur nahstöchiometrischen Verbrennung von flüssigem oder gasförmigem Brennstoff
DE29909302U1 (de) * 1999-05-27 1999-10-07 Man B & W Diesel Ag, 86153 Augsburg Gebläse mit einem Gebläserad, das in einem in mindestens zwei Gehäuseteile geteilten Gehäuse drehbar gelagert ist
DE29909301U1 (de) * 1999-05-27 1999-10-07 Man B & W Diesel Ag, 86153 Augsburg Gebläse mit einem Antrieb
EP1247988A1 (de) 2001-04-05 2002-10-09 PUNKER GmbH & CO. Gebläseanordnung, insbesondere Brennergebläse für Heizungsanlagen
DE10313054B4 (de) * 2003-03-24 2012-10-04 Motoren Ventilatoren Landshut Gmbh Radialgebläse
DE102006061756A1 (de) * 2006-12-28 2008-07-03 Alfred Kärcher Gmbh & Co. Kg Radialgebläse und mit einem Radialgebläse versehenes Hochdruck-Reinigungsgerät
WO2017119475A1 (ja) * 2016-01-07 2017-07-13 株式会社デンソー 送風機
CN114060319A (zh) * 2020-08-10 2022-02-18 佛山市顺德区美的洗涤电器制造有限公司 离心风机和抽油烟机
CN114076122B (zh) * 2020-08-10 2023-06-30 佛山市顺德区美的洗涤电器制造有限公司 导风圈、离心风机和抽油烟机

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH411207A (de) * 1962-05-25 1966-04-15 Helmbold Theodor Ing Dr Gebläse mit trommelförmigem Läufer
NL6500168A (da) * 1964-05-08 1965-11-09
DE1808829C3 (de) * 1968-11-14 1974-10-03 Dietrich Dr.-Ing. 5440 Mayen Haase Radial ventilator
DE2160047B2 (de) * 1971-12-03 1974-07-25 Dietrich Dr.-Ing. 5440 Mayen Haase Radialgebläse
FR2212864A5 (da) * 1972-12-29 1974-07-26 Chauffage Automatique
DE2540580C3 (de) * 1975-09-11 1983-12-01 Abig Werke Carry Gross GmbH & Co KG, 7770 Überlingen Radialventilator
DE3226217A1 (de) * 1981-08-14 1983-03-03 Oertli AG Dübendorf, 8600 Dübendorf Radialgeblaese, insbesondere mit trommellaeufer

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1002957A2 (de) * 1998-11-20 2000-05-24 PUNKER GmbH & CO. Radialgebläse
EP1002958A2 (de) * 1998-11-20 2000-05-24 PUNKER GmbH & CO. Radialgebläse
EP1022469A1 (de) 1999-01-20 2000-07-26 PUNKER GmbH & CO. Radialgebläse
EP1022470A1 (de) 1999-01-20 2000-07-26 PUNKER GmbH & CO. Radialgebläse
US6604906B2 (en) 2000-08-04 2003-08-12 Calsonic Kansei Corporation Centrifugal multiblade blower

Also Published As

Publication number Publication date
DE9216709U1 (de) 1993-02-11
DK0589300T3 (da) 1997-04-14
EP0589300A1 (de) 1994-03-30
DE4232178C1 (de) 1993-12-23
ATE146259T1 (de) 1996-12-15
DE59304734D1 (de) 1997-01-23

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