EP0228739A2 - Soufflante avec un boîtier substantiellement de forme carrée - Google Patents

Soufflante avec un boîtier substantiellement de forme carrée Download PDF

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Publication number
EP0228739A2
EP0228739A2 EP86202242A EP86202242A EP0228739A2 EP 0228739 A2 EP0228739 A2 EP 0228739A2 EP 86202242 A EP86202242 A EP 86202242A EP 86202242 A EP86202242 A EP 86202242A EP 0228739 A2 EP0228739 A2 EP 0228739A2
Authority
EP
European Patent Office
Prior art keywords
impeller
axial
blower
blower according
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.)
Withdrawn
Application number
EP86202242A
Other languages
German (de)
English (en)
Inventor
Raimünd Engelberger
Siegfried Dr. Harmsen
Hilmar Kirchgessner
Josef Schneider
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.)
Ebm Papst St Georgen GmbH and Co KG
Original Assignee
Papst Motoren GmbH and Co KG
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 Papst Motoren GmbH and Co KG filed Critical Papst Motoren GmbH and Co KG
Publication of EP0228739A2 publication Critical patent/EP0228739A2/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Withdrawn legal-status Critical Current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
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/52—Casings; Connections of working fluid for axial pumps
    • F04D29/522—Casings; Connections of working fluid for axial pumps especially adapted for elastic fluid pumps
    • F04D29/526—Details of the casing section radially opposing blade tips

Definitions

  • the invention relates to a blower according to the preamble of claim 1.
  • Aforementioned blower have been equipped with so-called radial impellers, that is, the air in the impeller itself is deflected from the intake direction by 90 0 in the Ausblasebene.
  • radial impellers that is, the air in the impeller itself is deflected from the intake direction by 90 0 in the Ausblasebene.
  • axial fans are known from German Offenlegungsschrift 22 57 509 (DE-413); similar also from DE-05 21 39 036 (DE-409).
  • a classic radial impeller was used, in which the flow is deflected by 90 ° within the impeller.
  • DE-AS 15 03 609 speaks of the fact that the medium being conveyed is deflected in the first part of the impeller and leaves the impeller with a radial flow component. After the task described there, this solution seems to be particularly useful for very high printing requirements.
  • This previously known solution also has a housing ring which widens conically in the conveying direction and extends approximately over half the axial width of the impeller and because of this extension should not allow the radial flow component in the region of the impeller. This solution leaves much to be desired in terms of low noise.
  • DE-PS 634 449 shows a spiral housing in which the air flow is deflected in the radial direction by means of strongly rounded blades in the central region thereof.
  • the impeller used here is also formally an axial wheel, so to speak, but the blades themselves continue to feed radially into the flow space via their radial outer edges - analogous to the two solutions described last.
  • the tube which extends from an inlet plane and extends into the axial center of the blades and is tapered in the direction of flow.
  • FIGS. 1 to 3 show a first embodiment.
  • 1 shows a top view of the air inlet plane 7, in FIG. 2 the view according to arrows II in FIGS. 1 and 2, that is to say the outlet opening 32 and in FIG. 3 a top view of the closed second main surface or rear wall 6 of the housing.
  • FIG. 2 shows a partial section on the right according to arrows II-II of FIG. 3.
  • FIGS. 1 and 2 show a central drive motor 8 which is advantageously designed as a so-called external rotor motor. He carries five axial blades 9, which are inclined by approximately 45 ° and are slightly curved.
  • the impeller is advantageously a one-piece plastic part with a cup-shaped hub, which is placed over the motor and integrally molded with plastic wings 9.
  • the drive motor located within the impeller hub 8 is held by the closed base plate 6 via screw elements 25, 26 by its stator.
  • the inner stator, which is located under the impeller hub 8, is held via the flange part 28 and the entire impeller with rotor is also held in a wire-supported manner via the plate 29.
  • the blowing direction is indicated by the arrows W.
  • the air inlet level 7 closes off with the housing.
  • the head of the impeller hub and the inlet-side blade edges 21 also lie in this plane.
  • the inlet curve is on the inlet side 12. Similar relationships are shown in FIG.
  • the air duct around the blades 9 is a cylinder 39 with an inner diameter 27. In a successful embodiment, it is 115 mm.
  • the impeller diameter 24, which belongs to it, has about 112 to 113 mm. This means that there is an air gap of 1 mm radially outside between the blades and the surrounding wall. On the one hand, this is justifiable in terms of flow quality and also in terms of manufacturing effort. The smaller this gap is, the better it is Current, but the more expensive it is to manufacture.
  • the walls 2, 3, 4 are therefore closed side surfaces, while the side surface 5 is open.
  • the air flows freely through the side surface 5 in the area of the axial height 32.
  • the dimension of the axial partial height 32 is 17 mm, while the upper axial partial dimension 31 is 22 mm.
  • the blow-out opening 32 in the plane of the side face 5 thus begins in the area of the blow-out blade edges 19, as the top view of the side face 5 in FIG. 2 shows. 2 is a partial section.
  • the upper surface which in partial section shows the wall ring 39 with the inlet-side and outlet-side rounding 12, 13 with a radius of curvature of approximately 5 mm in the exemplary embodiment, surrounds the blades (of course over the entire circumference) and on the blow-out side, namely the side surface 5 , almost half of this side surface is free as an outlet.
  • the closed inner wall surfaces 2, 3, 4 are set back by the flow wall ring 39 with the inner diameter 27 by a certain amount, so that the flow can initially develop into a somewhat larger cross section after leaving the impeller in the axial direction.
  • corner areas between the rectangular inner surfaces of the walls 2, 3 and 4 are rounded from the center of the wall 3 to the center of the wall 2 and to the center of the wall 4 such that the distance between this inner wall surface of the flat wall 2, 3 and 4 to the wall ring with the inner diameter 27 is kept approximately the same, ie the wall is rounded from center to center, in a manner not shown in FIGS. 1 to 3 ..., the center of the circle being the axis of rotation.
  • the full axial impeller dimension of 22 mm is (seen axially) behind the closed area of the side surface 5 with the height 31.
  • Figures 3 to 3 show the first embodiment in half natural size.
  • FIGS. 4 to 9 the same reference numbers as in FIGS. 1 to 3 are used for the parts having the same effect.
  • the impeller diameter is somewhat further reduced compared to the outer housing dimension (it is 67% of the same) and the speed (approx. 2300 rpm) of this smaller axial impeller is greater than the speed (approx. 2000 rev / min.) of the impeller according to Fig 1 to 3 of the first embodiment; embodiment, the diameter of which is large (83% of the G e-phaseseterrorismes 22).
  • the second embodiment is sufficient for The change in low noise is still very good, despite the pressure requirement being about twice as high as that of the first embodiment.
  • the eccentric position of the impeller in the housing cuboid additionally used in the second exemplary embodiment is known per se and still results in a certain improvement in the air performance with still low noise.
  • the characteristic resistance curves AW1 and AW2 are shown in broken lines for two specific applications.
  • AX1 is the blower characteristic for the first exemplary embodiment.
  • the operating point AP1 can also be operated with a radial fan wheel according to the characteristic curve RL. But the noise is far too high.
  • the axial wheel according to the first embodiment in the generic blower is operated at an increased speed, so that the device characteristic curve AX1 'would then apply, then the operating point AP2 of the resistance characteristic curve AW2 could also be used.
  • an arrangement according to the invention constructed according to embodiment 2 is better for this application.
  • the characteristic curve AX2 corresponds to this second exemplary embodiment and, with a further reduced impeller diameter at a somewhat higher speed, a very good noise behavior is obtained despite the increased pressure requirement (cf. above values). In this comparison there are practically the same outer dimensions of the housing cuboid.
  • FIG. 4 shows, similar to FIG. 2, a partial section through a complete blower according to the second embodiment. It is similar to that described in German Patent 22 57 509, the fan housing as a one-piece plastic part with the walls 2, 4, the front plate 70 and the flow ring 39 designed half-shell and screwed against the base plate 6, which is designed as a simple stamped and bent part. On the latter is the entire impeller with the coaxial concentric driving Electric motor which, as an external rotor motor as in FIG. 2, is mounted with screws 25, 26 against a conical recessed annular support plate 129, which is stamped out of the base plate 6 and is spaced from the inflow plane by the distance 62. The distance 62 is held so that it corresponds to the optimal axial position of the existing fan wheel 8, 9.
  • the inner stator of the external rotor motor has a flange plate 28 which is formed in one piece with the inner bearing support tube element 128 of the drive motor, so that the screws 25, 26 simply engage in the threads of the flange ring 28 through the openings 25 ', 26' of the mounting plate 129, the Heads of the screws 25, 26 of the conical recess.
  • FIG. 4 shows the optimal axial position of the impeller, the inlet-side blade edges 21 being provided near the inflow plane 7 but still in the region of the inlet curve 12, but in particular the outflow-side edges 19 with the edge 40 of the flow tube 39 complete axially.
  • FIG. 4 shows a somewhat less favorable position, which is somewhat better for the inflow conditions because the inlet-side edges 21 connect axially to the inflow curve 12, but in an embodiment according to the invention, the impeller with its blades 9 should at most be about as far protrude axially beyond the edge 40 of the flow tube 39, as shown in the right part of FIG. 4, namely with the outlet-side edges 19 at most approximately 2 mm or approximately 10% of the axial blade length. If one further axially spaced the outflow-side blade edge 19 from the end 40 of the flow tube 39, the noise will rise sharply.
  • FIG. 6 shows the full top view of the base plate 6, wherein, as mentioned, screws 25, 26 for mounting the flange through the openings 25 ', 26' of the annular, conically recessed holding plate 129, into which the base plate continues via a conical intermediate piece 67 28 of the engine.
  • FIGS. 4 to 6 show the natural size of the second embodiment
  • FIGS. 7 to 9 are reduced in comparison for reasons of the drawing.
  • the axis of rotation 100 both in the base plate of Figure 6 and in Figure 7 shows the position of the impeller 8, 9 in the housing 6, 77.
  • the eccentric offset is e.g. known from DE-PS 21 39 036, the distance between the housing walls increasing in the direction of flow. 7, the distances 112, 113, 114 are characterized by the length of their arrows, which increase between the flow ring 39 and the round wall 139.
  • the distances according to numbers 112, 113, 114 thus change approximately like 1 to 3 3, the outer round wall 139 being omitted on the outflow side over the entire width 120 of the outflow cross section.
  • the outflow on the side surface 5 is limited to the distance between the flow ring 39 and the base plate 39, but in the second embodiment, the full axial height 121 of the housing is free for the outflow cross section in the outflow plane, but the outflow takes place below the edge 40 certainly stronger in the area of the base plate 6. It is of secondary importance whether the outflow height 121 is used only over a part (for example part 32 of the housing height 33) or fully (at 133).
  • FIG. 7 shows a top view of the half-shell-like plastic housing which is screwed against the base plate 6 according to FIGS. 5/6, without this being shown.
  • a circumferential shoulder 44 is provided over the circumference, in which the metallic base plate 6 engages in a form-fitting manner before it is connected to the plastic holding shell 77 via the bolt-like elements 71 to 74 molded there is screwed.
  • the head surface 45 of the heel 44 which is then practically aligned with the outer wall of the base plate 6, is drawn in black.
  • FIG. 7 shows the eccentric position of the impeller axis 100 in the housing.
  • the axis 101 lying symmetrically in the housing 77 has practically the same distance from the outer walls 2, 4, which corresponds to the radius 111 of the round wall 139; the latter runs as a semicircle between the side walls 2, 4.
  • the axis 100 is shown in FIG. 7 in two steps counterclockwise (like the dashed direction of rotation of the impeller indicated by arrow 107) offset from the axis of symmetry 101.
  • the first step a in the outflow direction and the second step b to the left of the outflow direction each have a length of can 10% of the length of the radius 111.
  • the round wall 139 extends axially from the front plate 70 to the base plate 6, while the flow tube 39 is spaced with its edge 40 from the base plate 6.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
EP86202242A 1985-11-26 1986-11-26 Soufflante avec un boîtier substantiellement de forme carrée Withdrawn EP0228739A2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19853541787 DE3541787A1 (de) 1985-11-26 1985-11-26 Geblaese mit einem im wesentlichen quaderfoermigen gehaeuse
DE3541787 1985-11-26

Publications (1)

Publication Number Publication Date
EP0228739A2 true EP0228739A2 (fr) 1987-07-15

Family

ID=6286888

Family Applications (1)

Application Number Title Priority Date Filing Date
EP86202242A Withdrawn EP0228739A2 (fr) 1985-11-26 1986-11-26 Soufflante avec un boîtier substantiellement de forme carrée

Country Status (4)

Country Link
US (1) US4886415A (fr)
EP (1) EP0228739A2 (fr)
DE (1) DE3541787A1 (fr)
WO (1) WO1987003343A1 (fr)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
HU210777B (en) * 1989-09-29 1995-07-28 Micronel Ag Small ventilator
US5173020A (en) * 1991-02-19 1992-12-22 Carrier Corporation Collector silencer for a centrifugal compressor
SE469041B (sv) * 1991-08-16 1993-05-03 Nokia Data Ab Anordning foer uppbaerande av ett flaekthus med hjaelp av en elastisk ring
US5879232A (en) * 1997-03-25 1999-03-09 Tomkins Industries, Inc. Exhaust fan
US6328442B1 (en) 2000-01-31 2001-12-11 Hewlett-Packard Company Particulate filtering muffler
US7731477B2 (en) * 2006-01-23 2010-06-08 Erni Thomas W Insulated housing apparatus for use with an attic fan
US10052931B2 (en) * 2011-11-10 2018-08-21 Mitsubishi Electric Corporation Outdoor cooling unit in vehicle air-conditioning apparatus

Family Cites Families (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE634449C (de) * 1936-08-27 Sulzer Akt Ges Geb Ventilator mit mehrfluegeligem Propellerrad
CH168226A (de) * 1933-04-13 1934-03-31 Sulzer Ag Aus einem mehrschaufligen Propeller und einem Spiralgehäuse bestehender Ventilator.
US2325222A (en) * 1939-10-16 1943-07-27 Walter H Bretzlaff Air impelling apparatus
US2631775A (en) * 1949-08-23 1953-03-17 Price Electric Corp Packaged electrically operated ventilating fan
GB996056A (en) * 1961-06-20 1965-06-23 Philips Electronic Associated Blower
DE1428273C3 (de) * 1964-09-29 1973-01-04 Siemens Ag, 1000 Berlin U. 8000 Muenchen Flügelrad für einen geräuscharmen Axialventilator
DE1802523A1 (de) * 1968-10-11 1970-09-17 Gregor Freisberg Ventilator zum An- und Absaugen von Luft,Gasen,Daempfen usw.
DE2139036A1 (de) * 1971-08-04 1973-02-15 Papst Motoren Kg Luefter, insbesondere tischluefter
DE2257509C2 (de) * 1972-11-23 1982-09-02 Papst-Motoren GmbH & Co KG, 7742 St Georgen Radialgebläse
US4128364A (en) * 1972-11-23 1978-12-05 Papst-Motoren Kg Radial flow fan with motor cooling and resilient support of rotor shaft
US4073597A (en) * 1977-01-28 1978-02-14 The Celotex Corporation Fan housing assembly
FR2414649A1 (fr) * 1978-01-12 1979-08-10 Etri Sa Ventilateur axial a boitier polygonal plat, notamment carre
JPS5877200A (ja) * 1981-10-30 1983-05-10 Mitsubishi Electric Corp 送風機
JPS61200396A (ja) * 1985-02-28 1986-09-04 Mitsubishi Electric Corp 送風機
JPH0635880B2 (ja) * 1985-02-28 1994-05-11 三菱電機株式会社 送風機
JPH0635879B2 (ja) * 1985-02-28 1994-05-11 三菱電機株式会社 送風機

Also Published As

Publication number Publication date
DE3541787A1 (de) 1987-06-04
US4886415A (en) 1989-12-12
WO1987003343A1 (fr) 1987-06-04

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Inventor name: SCHNEIDER, JOSEF

Inventor name: HARMSEN, SIEGFRIED, DR.

Inventor name: ENGELBERGER, RAIMUEND

Inventor name: KIRCHGESSNER, HILMAR