EP1582750B1 - Boitier et soufflante avec un boitier et une roue - Google Patents

Boitier et soufflante avec un boitier et une roue Download PDF

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Publication number
EP1582750B1
EP1582750B1 EP20050005792 EP05005792A EP1582750B1 EP 1582750 B1 EP1582750 B1 EP 1582750B1 EP 20050005792 EP20050005792 EP 20050005792 EP 05005792 A EP05005792 A EP 05005792A EP 1582750 B1 EP1582750 B1 EP 1582750B1
Authority
EP
European Patent Office
Prior art keywords
wall
housing
peripheral wall
flow
impeller
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 - Fee Related
Application number
EP20050005792
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German (de)
English (en)
Other versions
EP1582750A3 (fr
EP1582750A2 (fr
Inventor
Christian Dipl.-Ing. Grömmer
Jörg Dipl.-Ing. Kilian
Werner Schwahn
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.)
Mahle Behr GmbH and Co KG
Original Assignee
Behr GmbH and Co KG
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Filing date
Publication date
Application filed by Behr GmbH and Co KG filed Critical Behr GmbH and Co KG
Publication of EP1582750A2 publication Critical patent/EP1582750A2/fr
Publication of EP1582750A3 publication Critical patent/EP1582750A3/fr
Application granted granted Critical
Publication of EP1582750B1 publication Critical patent/EP1582750B1/fr
Expired - Fee Related 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
    • 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
    • F04D29/40—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
    • F04D29/4226—Fan casings
    • F04D29/4233—Fan casings with volutes extending mainly in axial or radially inward direction

Definitions

  • the invention relates to a housing for a radial fan with a flow channel which extends between an input wall and a rear wall arranged at a distance therefrom and a peripheral wall connecting the same, wherein an exhaust opening for the flow channel is arranged in the region of the peripheral wall.
  • a housing for a radial fan with a flow channel which extends between an input wall and a rear wall arranged at a distance therefrom and a peripheral wall connecting the same, wherein an exhaust opening for the flow channel is arranged in the region of the peripheral wall.
  • Such housing with a radial wall surrounding the radial fan peripheral wall are also referred to as spiral housing.
  • the invention relates to an impeller for such a housing and a radial fan with a housing and an impeller.
  • Radial blowers according to the prior art are suitable in many forms and sizes for the promotion of fluid media in the form of air, gas or steam. Accordingly, such fans find many applications, especially in the field of air conditioning and heating systems, eg. B. in vehicles. Larger embodiments of such radial blowers are used for example in power plant construction.
  • an axially sucked air flow is usually performed after entering an axially mounted impeller and there over in Impeller arranged impeller blades or rows of blades to a radial Ausblasung deflected by 90 °. That is, the axially sucked by the impeller air flow is conveyed by means arranged in the impeller conveyor blades or rows of blades to its peripheral region and thus deflected radially. Thereafter, the air stream escaping from the impeller is further conveyed tangentially along a housing surrounding the impeller, in particular along its peripheral wall, said housing often having the form of a spiral. From the spiral, the air flow is conveyed via the so-called discharge nozzle into a possible air distribution system.
  • Impeller loading and impeller flow are uneven. On the frame side is due to insufficient deflection from the axial to the radial direction much less promoted as the blower motor side.
  • the distribution of the volute casing volume over the impeller width does not take into account these flow conditions in the prior art.
  • In the spiral housing secondary flows from the motor side to the frame side occur. In the motor-side, but more pronounced in the frame-side edge regions of the spiral housing of the main flow secondary vortex are superimposed. These flow conditions are at the expense of the efficiency of the radial fan.
  • the efficiency can be defined as the ratio of the fan's air output to the fan's shaft power, with the fan's shaft power defined as the product of torque and angular velocity.
  • All known from the prior art embodiments are provided with a substantially rectangular spiral housing.
  • all previously known flow channels are provided in a housing with a substantially rectangular cross-section, as it is for example in the EP 11 068 37 A1 is shown.
  • Such right-angled spiral casings ie spiral casings with a rectangular cross-section for the flow channel, as in FIG EP 1 106 837 A1 have uneven impeller loads and impeller flows because the front and rear sidewalls are not axially inclined in the flow direction and the radial distance between the impeller outlet or exhaust port and the peripheral wall of the housing in the axial direction is constant over the impeller width, although the impeller flow is along the impeller width is uneven.
  • a blower of a motor vehicle air conditioner which has a flow channel which increases in the width dimension and the volume at its outer periphery.
  • the invention is based on the object to provide a housing for a radial fan, in which over the prior art, a reduction of the secondary flows is achieved in the spiral housing.
  • a radial blower with a housing and a particularly suitable impeller is to be specified.
  • the flow channel of the housing expands radially from the input wall toward the rear side wall.
  • the side walls can be inclined axially in the flow direction.
  • the invention is based on the consideration that a housing for a radial fan, in particular a spiral housing, where the largest mass flow of the fluid medium to be conveyed occurs as a result of the deflection, should provide the larger volume of space and vice versa. That is, in the area of the volute casing, as a result of the mass flow with a smaller volume of space, a reduction in the volume of the room and, with a larger volume of volume, an increase in the volume of the space should take place so that the flow cross-section remains constant.
  • the front suction-side regions of the housing are generally less exposed to the fluid medium than axially lower regions of the housing. In order to achieve a homogenization of the flow through the housing taking advantage of the entire housing width, it is therefore provided to adapt the housing so that where the largest mass flow is to be conveyed, corresponding volume of space is created.
  • the housing is spirally circulating flow channel designed such that it expands from the input wall in the direction of the rear side wall or vice versa.
  • the peripheral wall bounding the flow channel is inclined about its midpoint in the width. The inclination of the peripheral wall can also be done by a deviating from the center axis of rotation.
  • the housing has the shape of a linearly extended spiral or a logarithmic spiral with respect to the radial extension in the fulcrum.
  • the widening of the flow channel expediently takes place in such a way that the widening is formed at at least one point in the course of the flow channel over the entire or a part of the width of the flow channel. That is, the expansion over the width of the flow channel, which corresponds approximately to the width of the peripheral wall, thus takes place in a significant part and is not limited, as in the prior art, on edge regions of the housing, for example by rounding corners or the like. Depending on the embodiment, the rounding of the corners can take place with correspondingly constant corner radii. Alternatively, the corner radius may vary along the circumference of the housing. For example, the corner radius of the housing tongue in the direction of the exhaust opening increases.
  • a widening of the flow channel is preferably achieved in that the rear side wall and the suction-side inlet wall spaced therefrom, including the peripheral wall, are arranged at an angle to one another, including the peripheral wall, over at least one or both sides over the entire area or only over partial areas of the spiral course of the flow channel.
  • the spiral housing can be made wider than the impeller.
  • the volute casing can be designed to be axially expanded on one or both sides.
  • At least at one point of the flow channel starting from the suction-side inlet or side wall in the direction of the rear engine-side side wall is a radial expansion.
  • a radial expansion Under an at least partial expansion of the flow channel is understood that this only on a portion of the spiral Circulation expands.
  • the flow channel can be completely provided over its entire circumference with a radial expansion extending over its width.
  • the input wall and the peripheral wall are suction side to each other to form an obtuse angle
  • the rear side wall and the peripheral wall are arranged to each other to form an acute angle, so that an expansion of the flow channel is given.
  • a cross-sectional shape for the flow channel a trapezoidal shape, in particular an irregular trapezoidal shape, or a triangular shape or a parallelogram.
  • An irregular trapezoid or a triangle is simulated in such a way that the wider side of the geometric shape is formed essentially by the rear side wall, wherein the front short side or a triangular tip forms part of the input wall of the Housing forms.
  • a parallelogram a widening of the flow channel takes place in the area of the rear side wall.
  • the peripheral wall of the input wall in the direction of the rear side wall is step-shaped.
  • the flow channel is stepped on the side or circumferentially, so that in the axial direction z. B. a rear stage has a greater radial extent than a front stage.
  • each step may preferably be designed according to one of the above-mentioned geometric shapes, d. H. radially widening towards the rear side wall.
  • the circumferential wall in the width has an inclination of greater than 0 ° to a maximum of 45 °.
  • the peripheral wall is preferably rectilinear.
  • the peripheral wall may be arcuate, in particular arcuate inwardly or outwardly, or may have another suitable shape.
  • the flow channel is divided one or more times in the direction of flow. By subdivision, for example by means of partitions or multiple vanes, secondary flows are prevented. In addition, a separate volute casing design for each individual channel cross-section is possible, so that flow losses are reduced
  • an axial inlet opening is preferably provided in the inlet wall on the suction side.
  • the axial inlet opening may be bead-shaped.
  • the blow-out opening is advantageously arranged radially or tangentially in the region of the peripheral wall.
  • the exhaust opening is perpendicular to the main flow direction in the spiral housing.
  • the exhaust opening in the Circumferential wall arranged which is preferably round, but may also have another expedient shape.
  • An impeller for a radial blower is preferably formed by a number of blades driven in rotation about an axis of rotation, in particular between an input wall and a rear side wall, whose blade ends open into a flow channel arranged along a circumferential wall which connects radially to the input wall and the rear side wall the respective blade end axially expanding, in particular from the input wall in the direction of the rear side wall extends.
  • the respective blade end can increase radially in the inner and / or outer diameter.
  • the impeller is provided with at least one row of blades extending about the axis of rotation. If there are two rows of blades running around the axis of rotation, they may be bladed differently.
  • the blade ends of adjacent blade rows of the input wall in the direction of the rear side wall are stepped to each other, in particular formed axially widening.
  • the rows of blades are connected via a hub with the blower motor.
  • the hub may have openings for fan motor cooling and may be conveniently shaped.
  • an impeller and a housing are advantageously adapted to each other, according to the form described above.
  • the impeller and the front and / or rear side wall are in the entry or exit or both sides in a plane.
  • secondary flows are reduced by closing the housing.
  • the impeller preferably has a profiled blading, which divides the blade channel into a convergent channel part and a divergent channel part.
  • the flow In a first short - the convergent - channel part, the flow is accelerated and unguided, in the second straight or slightly curved - the divergent - channel part, the flow is delayed.
  • Fig. 1 shows a perspective view of a housing 1 for a radial blower 2.
  • the housing 1 comprises a rear side wall 3 and a spaced apart suction side input wall 5. Axial in the inlet wall 5 suction side, an inlet opening 7 (also called frame) arranged. Between the rear side wall 3 and the front entrance wall 5, connecting them, a circumferential wall 11 extends along the housing circumference 9 to form a flow channel 13.
  • the housing 1 - also called spiral housing - is limited radially along its housing circumference 9 of the spiral-shaped peripheral wall 11 in the present embodiment. That is, to form a spiral peripheral wall 11, the flow channel 13 increases along the flow direction R in its dimensions in the direction of a discharge opening 15 arranged perpendicular to the circumferential wall 11. This is in the Fig. 1 indicated by four polygons forming the respective cross section of the flow channel 13 at respective positions P0 to P3. That is, the dimensions, in particular the cross-section of the flow channel 13, increase from the position P0 in the direction of the exhaust opening 15.
  • the spiral shape of the housing 1 (also called spiral housing) is suitably adapted accordingly to the flow of the fluid medium and the resulting pressure load.
  • the rear side wall 3, the input wall 5 and the peripheral wall 11 form the flow channel 13.
  • the rear side wall 3 has an opening for driving by means of an electric motor and the cooling thereof.
  • the suction-side input wall 5 is provided with the inlet opening 7, which is arranged axially symmetrically or asymmetrically about a rotation axis 17 of the housing 1.
  • the inlet opening 7 may have further Zargenformen and geometric designs.
  • the rear side wall 3 and the input wall 5 are spaced from each other by the peripheral wall 11 of the housing 1.
  • the course of the flow of the fluid medium is in the Fig. 1 indicated by flow arrows S1 and S2.
  • the fluid medium usually air, gas or steam, is sucked in axially according to the flow arrow S1 along the axis of rotation 17 through the inlet opening 7 of the housing 1.
  • the fluid Medium is then passed radially outwardly into the flow channel 13 along the radial extent, in particular the peripheral wall 11 of the housing 1, and thus along the circumferential course of the flow channel 13 and finally through the exhaust port 15 in this case along the main flow direction R from the housing first and thus flowed out of the radial fan 2.
  • the blow-out opening 15 may also be arranged radially at a suitable point tangentially in the region of the circumferential wall 11 instead of a vertical arrangement.
  • the circumferential wall 11 forms an obtuse angle ⁇ with the suction-side inlet wall 5.
  • the peripheral wall 11 forms an acute angle ⁇ in this area. In this way, at least partially along the course of the circumferential wall 11, a widening of the flow channel 13 from the input wall 5 in the direction of the rear side wall 3, since both the input wall 5 and the rear side wall 3 with the peripheral wall 11 form no right angle.
  • the peripheral wall 11 is thus arranged obliquely to the input wall 5 and the rear side wall 3.
  • the opening or flow cross-section of the flow channel 13 forms a polygonal shape, in particular a trapezoidal shape.
  • the flow cross-section of the flow channel 13 may have a triangular shape or a parallelogram shape.
  • the flow channel 13 can be completely widened along the circumferential wall 11.
  • the flow channel 13 may be formed widened only in partial areas.
  • the expansion can take place in the opposite direction. The widening of the flow channel 13 takes place by tilting the peripheral wall 11 to its width midpoint. Alternatively, the inclination of the Circumferential wall 11 may be formed at a distance from the width center pivot point.
  • a radial fan 2 is shown in section with a spiral housing 1 and an impeller 19 with radius r D.
  • the flow channel 13 is formed only partially expanded along the peripheral wall 11.
  • the blow-out opening 15 is the widening of the flow channel 13 0 °. That is, the circumferential wall 11 forms with the input wall 5 and the rear side wall 3 in each case an angle of 90 °, so that the input wall 5 and the rear side wall 3 are arranged plane-parallel to each other.
  • the area B1 may be widened.
  • the widening of the flow channel 13 along the circumferential wall 11 increases by varying its inclination in the flow direction R along the arrow P2 from 10 ° to 40 ° or to 50 ° (peripheral wall position).
  • one of the walls of the housing 1 - the input wall 5 and / or the rear side wall 3 - are made oblique to the vertical and thus inclined.
  • the side wall 3 or the input wall 5 can be inclined along an extension which corresponds at most to the length of the circumferential wall 11.
  • an inclination of one of the side walls - input wall 5 or rear side wall 3 - to the vertical of up to 30 ° can also be achieved here.
  • an overall obtuse angle ⁇ between peripheral wall 11 and input wall 5 of 90 ° + 20 ° + 30 ° Reach 140 °.
  • Fig. 3 shows a possible embodiment of a radial blower 2 with a housing 1 and an impeller 19.
  • the impeller 19 and the housing 1 are arranged about an axis of rotation 17.
  • the fluid medium is sucked in axially on the suction side along a flow arrow S1 through the frame opening or inlet opening 7 by means of the impeller 19 and conveyed in the radial axial direction along a flow arrow S2 into the flow channel 13 arranged circumferentially along the circumferential wall 11.
  • the cross section of the flow channel 13 is formed trapezoidal to triangular. That is, the flow channel 13 is widened from the input wall 5 in the direction of the rear side wall 3.
  • the inclined position of the peripheral wall 11 and the rear side wall 3 is inclined in this embodiment against a usually rectangular orientation of peripheral wall and side wall.
  • the widening of the circumferential wall 11 to the horizontal can be up to 45 °, ie the peripheral wall 11 assumes, for example, with respect to the input wall 5 at an expansion of 20 ° an obtuse angle ⁇ of 110 °.
  • the inclination of the input wall 5 is 0 ° in this example.
  • the inclination of the rear side wall 3 may vary between a range of about 0 ° to 30 °.
  • the acute angle ⁇ between the circumferential wall 11 and the rear side wall 3 is 40 ° to 70 °.
  • the expansion of the peripheral wall 11 is 20 °.
  • Fig. 4 shows a further embodiment of a radial fan 2 with impeller 19 and housing 1.
  • the housing 1 and its flow channel 13 extending therein are formed only partially obliquely.
  • the housing 1 is configured at right angles, ie, the circumferential wall 11 is arranged at right angles to the input wall 5 and to the rear side wall 3.
  • the tongue region Z as shown by the dashed line, be formed stepwise.
  • the housing 1 Compared to the rectangular tongue region Z, the housing 1, in particular its peripheral wall 11 and thus its flow channel 13, is formed in a stepped and trapezoidal manner in the area above the axis of rotation 17. This area of the circumferential wall 11 above the axis of rotation 17 is also called the discharge nozzle area D.
  • the peripheral wall 11 is formed with a first trapezoidal step T1 in the region of the inlet wall 5.
  • a second trapezoidal step T2 connects directly to the first step T1.
  • further stages Tn may be possible.
  • the width of the steps may vary over the circumference 9.
  • the edges of the input wall 5 and / or the rear side wall 3 are additionally rounded.
  • the impeller 19 is rotationally driven about the rotation axis 17 and has a radius r D , so that blade ends Er of the impeller 19 open into the flow channel 13.
  • Fig. 5a to 5d schematically show various embodiments of further radial fan 2 with different oblique housings 1a to 1c and oblique flow channels 13a to 13f.
  • the housing 1a with the flow channel 13a in this case has a rather parallelogram-like opening cross-section.
  • On the flow output side a bead frame is formed.
  • the housing 1b with the flow channel 13b provides a trapezoidal to triangular opening or flow cross-section.
  • the housing 1 c with the flow channel 13 c is a rectangular housing with an oblique side wall 3 with the flow input side bead frame.
  • impeller 19 In the respective housing 1a to 1c, a driven about the rotation axis 17 impeller 19 is arranged, which has a trapezoidal cross section depending on the embodiment.
  • a driven about the rotation axis 17 impeller 19 In the Fig. 3 and 4 is an impeller 19 with rectangular cross-section shown in combination with a housing 1 having a skewed cross-section.
  • a flow channel 13 which is widened in the direction of the rear side wall 3 by an inclined position of the circumferential wall 11 causes a widened volume in the region of the rear side wall 3 and, as a result, a particularly strong flow, so that secondary flows are reduced.
  • FIG. 5b to 5d Further geometric cross-sectional shapes for a widening of a flow channel 13d to 13f are shown.
  • the hatched areas represent the respective flow channel 13d to 13f in the region of the circumferential wall 11 between the input wall 5 and the rear side wall 3.
  • the front input wall 5 is inclined
  • this is designed bead-shaped to avoid delamination on the frame.
  • the front side wall or entrance wall 5 may be inclined axially toward the rear side wall 3 to improve impeller loading and to prevent secondary flow.
  • the impeller 19 may be equipped on the suction side with an arcuate cover plate. Also additional sealing edges 22 are possible, for. B. positioned on the impeller 19, as in Fig. 5a represented, or according to the volute casing 1.
  • the volute casing 1 may be formed wider than the impeller 19.
  • the spiral housing 1 is extended on one side or both sides axially.
  • the corners or edges of the peripheral wall 11 may additionally be rounded.
  • the corners along the housing periphery 9 may have a constant radius or a varying radius. At a varying radius, the corner radius along the housing periphery 9 increases from the tongue toward the exhaust port 15.
  • Fig. 6 schematically shows a further preferred embodiment of a radial blower 2 with a housing 1 and an impeller 19.
  • the impeller 19 is seated on a along an axis of rotation 17 arranged shaft, which is driven by an electric motor M.
  • a circumferential wall 11 which surrounds the housing 1 spirally and the associated flow channel 13 are stepped, wherein, starting from the input wall 5 in the direction of the rear side wall 3, a widening results, in that the steps T1 and T2 are formed radially increasing.
  • the respective stage T1 and T2 can also be widened from the input wall 5 in the direction of the rear side wall 3, ie the stages T1 and T2 would be inclined (not shown in detail), wherein the expansion may be different for each stage.
  • the peripheral wall 11 may be formed in various ways, for. B. arcuate (inwardly or outwardly arcuate), linear or cupped.
  • the rear side wall 3 of the housing 1 is additionally inclined to the vertical, so that the rear side wall 3 with the peripheral wall 11 forms an acute angle ⁇ .
  • the flow channel 13 and the exhaust opening 15 are divided in the embodiment.
  • a partition wall 21 is provided between the two stages T1 and T2 of the peripheral wall 11 and the stepped flow channel 13 in the region of the exhaust opening 15.
  • a guide vane for dividing the flow channel 13 into several Subchannels may be provided in different areas of the flow channel.
  • Fig. 6 could be adapted to be stepped in adaptation to the housing 1 shown here with a stepped peripheral wall 11 and the impeller 19.
  • the impeller 19 in a manner not shown on two axially in the flow direction R side by side on the axis of rotation 17 arranged rows of blades with increasing from the input wall 5 in the direction of the rear side wall 3 radius r D and thus corresponding to the stages T1 and T2 are executed.
  • FIGS. 7 and 8 show further embodiments of a housing 1 of a radial fan 2 in the radial section of the spiral housing 1.
  • the housing 1 in these embodiments is formed in each case two columns. Ie. It is sucked in via two inlet openings 7 axially in the front entrance wall 5 and the rear side wall 3.
  • This in Fig. 7 shown housing 1 in this case comprises a straight impeller 19 with a surrounding oblique or pointed roof-like spiral housing.
  • the housing 1 has there a large housing volume, where a high mass flow is promoted. As a result, secondary flow effects are reduced.
  • Fig. 8 shown housing 1 additional gap losses are reduced.
  • a straight oblique oblique impeller 19 is surrounded by the housing 1.
  • a fan motor may be positioned in one of the inlet openings 7 for cooling thereof.
  • the front input wall 5 and / or the rear side wall 3 and the corresponding blade end E B of the impeller may be arranged in a plane EB.
  • a holder 24 for a motor the fan motor
  • an opening 26 for cooling the fan motor is provided in the region of the impeller 19 of the rear side wall 3.
  • Fig. 10 shows an alternative embodiment for an impeller 19 with a blade row SR and a profiled blading.
  • the respective blades SS of the blade row SR are formed profiled, for example, formed curved forward or backward.
  • a blade channel SK is formed, which is subdivided into a first convergent channel part SK1 and into a second divergent channel part SK2.
  • An acceleration and deflection of the flow occurs in the first channel part SK1 and a delay of the flow in the second, approximately straight or slightly curved channel part SK2.
  • Such a profiled blading of the blade row SR allows the use of the fan 2 for the forward curved case, even at low speed level.
  • the space of the spiral housing can be made more flexible
  • adjacent blade row SR can be arranged offset relative to each other by half a blade pitch. That is, the blades SS of a blade row SR are offset - arranged in the distance between two blades SS of the adjacent blade row SR.

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Claims (18)

  1. Carter (1) pour une soufflante radiale (2) comprenant un conduit d'écoulement (13) qui est disposé le long d'une paroi circonférentielle (11) s'étendant radialement et reliant la paroi d'entrée (5) et la paroi latérale arrière (3) disposée à distance de celle-ci, et comprenant une ouverture d'évacuation d'air (15) prévue dans la zone de la paroi circonférentielle (11), pour le conduit d'écoulement (13), où le conduit d'écoulement (13) s'élargit radialement en direction de la paroi latérale arrière (3), à partir de la paroi d'entrée (5),
    caractérisé en ce que la paroi d'entrée (5) et la paroi circonférentielle (11) sont disposées, côté aspiration, en formant l'une par rapport à l'autre un angle obtus (α) qui est supérieur à 90°, et la paroi latérale arrière (3) et la paroi circonférentielle (11) sont disposées en formant l'une par rapport à l'autre un angle aigu (β) qui est inférieur à 90°.
  2. Carter selon la revendication 1, caractérisé en ce que le conduit d'écoulement (13) s'élargit radialement, au moins partiellement le long de son étendue, en direction de la paroi latérale arrière (3), à partir de la paroi d'entrée (5).
  3. Carter selon l'une ou l'autre des revendications 1 et 2, caractérisé en ce que le conduit d'écoulement (13) présente une section trapézoïdale, une forme de parallélogramme ou bien une forme de triangle.
  4. Carter selon l'une quelconque des revendications 1 à 3, caractérisé en ce que la paroi circonférentielle (11) s'étend de façon étagée en direction de la paroi latérale arrière (3), à partir de la paroi d'entrée (5).
  5. Carter selon l'une quelconque des revendications 1 à 4, caractérisé en ce que la paroi circonférentielle (11) s'étend en largeur, en ayant une inclinaison supérieure à 0.
  6. Carter selon l'une quelconque des revendications 1 à 5, caractérisé en ce que la paroi circonférentielle (11) s'étend en largeur, suivant une forme arquée ou de façon rectiligne.
  7. Carter selon l'une quelconque des revendications 1 à 6, caractérisé en ce que le conduit d'écoulement (13), vu dans la direction d'écoulement (R), est subdivisé de façon simple ou multiple.
  8. Carter selon l'une quelconque des revendications 1 à 7, caractérisé en ce qu'il est prévu une ouverture d'entrée axiale (7) dans la paroi d'entrée (5).
  9. Carter selon l'une quelconque des revendications 1 à 8, caractérisé en ce que l'ouverture d'entrée (7) est configurée en forme de renflement dans la zone de bordure.
  10. Carter selon l'une quelconque des revendications 1 à 9, caractérisé en ce que l'ouverture d'évacuation d'air (15) est disposée, dans la zone de la paroi circonférentielle (11), de façon radiale ou tangentielle.
  11. Soufflante radiale comprenant un carter selon l'une quelconque des revendications précédentes, caractérisée par un rotor comprenant un certain nombre d'ailettes disposées autour d'un axe de rotation (17), entre une paroi d'entrée (5) et une paroi latérale arrière (3), ailettes dont les extrémités (Er) débouchent dans un conduit d'écoulement (13).
  12. Soufflante radiale selon la revendication 11, caractérisée en ce que l'extrémité d'ailette respective (Ea) du rotor s'étend axialement, en particulier en s'élargissant axialement en direction de la paroi latérale arrière (3), à partir de la paroi d'entrée (5).
  13. Soufflante radiale selon la revendication 11 et / ou 12, caractérisée en ce qu'il est prévu au moins une rangée d'ailettes s'étendant autour de l'axe de rotation (17).
  14. Soufflante radiale selon l'une quelconque des revendications 11 à 13, caractérisée en ce qu'il est prévu au moins plusieurs rangées d'ailettes s'étendant autour de l'axe de rotation (17), rangées d'ailettes qui sont ailetées le cas échéant de façon différente.
  15. Soufflante radiale selon la revendication 14, caractérisée en ce que les extrémités d'ailettes (Er) de rangées d'ailettes adjacentes sont étagées les unes par rapport aux autres, configurées en particulier en s'élargissant axialement en direction de la paroi latérale arrière (3), à partir de la paroi d'entrée (5).
  16. Soufflante radiale selon l'une quelconque des revendications 11 à 15, caractérisée en ce que la rangée d'ailettes respective présente un ailetage profilé.
  17. Soufflante radiale selon l'une quelconque des revendications 11 à 16, caractérisée en ce que l'ailetage présente un profilage, et le profilage forme un conduit d'ailette convergent / divergent, où l'ailetage est recourbé vers l'avant.
  18. Soufflante radiale selon l'une quelconque des revendications 14 à 17, caractérisée en ce que des rangées d'ailettes adjacentes sont disposées en étant décalées d'un demi-écartement d'ailettes, les unes par rapport aux autres.
EP20050005792 2004-03-22 2005-03-17 Boitier et soufflante avec un boitier et une roue Expired - Fee Related EP1582750B1 (fr)

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Publication number Priority date Publication date Assignee Title
JP5739981B2 (ja) 2010-04-06 2015-06-24 スリーエム イノベイティブ プロパティズ カンパニー 成形スクロールプロファイルを有する放射ブロワー
CN212337718U (zh) * 2019-12-13 2021-01-12 绍兴阿利卡电器有限公司 一种用于油烟机、集成灶内的大风压蜗壳
CN113091131A (zh) * 2021-03-24 2021-07-09 青岛海尔空调器有限总公司 空调内机及空调器

Family Cites Families (6)

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Publication number Priority date Publication date Assignee Title
US5188508A (en) * 1991-05-09 1993-02-23 Comair Rotron, Inc. Compact fan and impeller
US5743710A (en) * 1996-02-29 1998-04-28 Bosch Automotive Motor Systems Corporation Streamlined annular volute for centrifugal blower
EP0846868A3 (fr) * 1996-12-05 1999-02-03 General Motors Corporation Unité de soufflante centrifugale
US6042335A (en) * 1998-05-04 2000-03-28 Carrier Corporation Centrifugal flow fan and fan/orifice assembly
US6224335B1 (en) * 1999-08-27 2001-05-01 Delphi Technologies, Inc. Automotive air conditioning fan assembly
DE20309621U1 (de) * 2003-03-24 2003-09-18 Motoren Ventilatoren Gmbh Radialgebläse

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EP1582750A2 (fr) 2005-10-05
DE502005007543D1 (de) 2009-08-06

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