EP3020979B1 - Ventilateur à pales multiples - Google Patents

Ventilateur à pales multiples Download PDF

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Publication number
EP3020979B1
EP3020979B1 EP13889351.6A EP13889351A EP3020979B1 EP 3020979 B1 EP3020979 B1 EP 3020979B1 EP 13889351 A EP13889351 A EP 13889351A EP 3020979 B1 EP3020979 B1 EP 3020979B1
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EP
European Patent Office
Prior art keywords
impeller
region
peripheral side
blades
internal space
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.)
Active
Application number
EP13889351.6A
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German (de)
English (en)
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EP3020979A4 (fr
EP3020979A1 (fr
Inventor
Yasuaki Kato
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Mitsubishi Electric Corp
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Mitsubishi Electric Corp
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Publication date
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Publication of EP3020979A1 publication Critical patent/EP3020979A1/fr
Publication of EP3020979A4 publication Critical patent/EP3020979A4/fr
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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
    • F04D29/32—Rotors specially for elastic fluids for axial flow pumps
    • F04D29/325—Rotors specially for elastic fluids for axial flow pumps for axial flow 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
    • F04D19/00—Axial-flow pumps
    • F04D19/002—Axial flow 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
    • 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
    • F04D29/26—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
    • F04D29/26—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
    • F04D29/30—Vanes
    • 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
    • F04D29/32—Rotors specially for elastic fluids for axial flow pumps
    • F04D29/38—Blades
    • F04D29/384—Blades characterised by form

Definitions

  • the present invention relates to a multiblade centrifugal blower.
  • Multiblade blowers are air blowers devised to attain a large flow rate based on a centrifugal blower.
  • An inner-outer diameter ratio of each blade is set relatively large in order to increase a diameter of an air inlet.
  • the large inner-outer diameter ratio causes reduction in length of the blade in cross section horizontal to a rotation axis.
  • the number of the blades is increased so as to prevent separation.
  • forward curved vanes are employed so as to increase an outlet absolute speed, and a scroll casing is provided so as to change high dynamic pressure into static pressure.
  • the multiblade blowers have simple configuration and are manufactured at low cost, and hence are widely used for general industrial applications, air conditioning applications, and the like.
  • An impeller arranged in the multiblade blower has a plurality of elongated blades arrayed in a circumferential direction, and entirely has a columnar shape when viewed in a rotation locus.
  • An air inlet is formed on one side of the column or each of end surface regions having a circular shape on both sides of the column, and an air stream flowing through the air inlet passes between the blades, and flows out from a side surface region of a cylindrical shape in the columnar shape.
  • JP H06 129388 A discloses a blower with a centrifugal fan.
  • US 6 345 956 B1 discloses an impeller of a blower having air-guiding ribs with geometrical configurations.
  • FR 2 155 668 A5 discloses an electrically motorised fan.
  • the flow passing through the axial-flow fan is applied with a swirling component from the axial-flow fan, and hence a vector of the flow varies between the front and back of the axial-flow fan. Therefore, even when the flow into the blades and the blade shape are appropriate on an upstream side of the axial-flow fan, the flow into the blades and the blade shape are inappropriate on a downstream side of the axial-flow fan. Thus, there is a problem in that the flow rate in accordance with the dimension of the multiblade blower in the rotation axis direction cannot be attained. Further, inappropriate flow into the blades and inappropriate blade shape cause a problem in that the separation at an inlet portion of the blade is significant to increase noise.
  • the present invention has been made to solve the problems as described above, and it is an object of the present invention to provide a multiblade blower capable of attaining the large flow rate while suppressing noise.
  • a multiblade blower as defined by the appended claims 1, 2 or 3.
  • the plurality of second-impeller blades each are constructed such that a swirling-direction component of a wake in a region on an outer peripheral side in the internal space of the first impeller is smaller than a swirling-direction component of a wake in a region on an inner peripheral side in the internal space.
  • the first impeller include a main plate fixed to a drive shaft, that the plurality of first-impeller blades be arranged along a periphery of the main plate, that the plurality of second-impeller blades connect together the drive shaft and the first-impeller blades, and that the plurality of first-impeller blades be held by the main plate and be also held by the second-impeller blades.
  • a distance in the first impeller from an end portion on the air inlet side to a position connected to the second impeller be from 0.5 time to 1.0 time as large as an outer diameter of the first impeller.
  • a dimension of the first impeller in a rotation axis direction be from 1.0 time to 1.5 times as large as the outer diameter of the first impeller.
  • the multiblade blower according to the present invention is capable of attaining the large flow rate while suppressing noise.
  • FIG. 1 is an external view of a multiblade blower according to a first embodiment of the present invention, for illustrating a state in which an air inlet described later corresponds to a front side of the drawing sheet and the multiblade blower is viewed toward the air inlet.
  • FIG. 2 is a view for illustrating a cross section of the multiblade blower taken along the line II-II of FIG. 1 .
  • a multiblade blower 1 is an air blower to be used in, for example, an air conditioner or a ventilation fan, and includes a casing 2, an impeller 3, and a drive motor 4 serving as a drive source.
  • the drive motor 4 and the impeller 3 share a rotation axis 5.
  • a direction parallel to the rotation axis 5 is referred to as a rotation axis direction.
  • a radiation direction of a straight line starting from the rotation axis 5 as the end point in a plane perpendicular to the rotation axis 5 is referred to as a radial direction.
  • a side of the radial direction, which is closer to the rotation axis 5, is referred to as an inner peripheral side.
  • a side of the radial direction, which is far from the rotation axis 5, is referred to as an outer peripheral side.
  • the casing 2 is, for example, a scroll casing, and includes an air inlet 6, a scroll wall 7, and an air outlet 8.
  • the scroll wall 7 forms a scroll shape as an enlarging air duct in a cross section perpendicular to the rotation axis 5.
  • the air inlet 6 is an opening formed by an annular portion having a bellmouth shape.
  • the air inlet 6 is formed on one side surface of the casing 2, and the rotation axis 5 extends to pass through the center of the opening.
  • the air outlet 8 is formed in a plane of the casing 2 in a swirling direction of the scroll shape.
  • the drive motor 4 is arranged on an outside of a side surface of the casing 2 on a side opposite to the air inlet 6.
  • a motor shaft 9 of the drive motor 4 passes through the casing 2 to extend along the rotation axis 5 inside the casing 2. Further, the motor shaft 9 serving as a drive shaft protrudes toward the air inlet 6.
  • the impeller 3 includes a first impeller 3a serving as a centrifugal fan such as a sirocco fan, and a second impeller 3b serving as an axial-flow fan, and is received in the casing 2.
  • the first impeller 3a includes a main plate 10 having a substantially disc-like shape, and a plurality of first-impeller blades 11.
  • the main plate 10 is fixed to the motor shaft 9 in the vicinity of an inner wall surface of the casing 2 on the side opposite to the air inlet 6.
  • the plurality of first-impeller blades 11 extend to be elongated along a direction of the rotation axis 5, and are positioned so as to form a cylindrical shape. Further, the plurality of first-impeller blades 11 are arranged along a periphery of the main plate 10, and are arrayed to be equiangularly separated from each other so as to form an annular shape. An annular member 12 for reinforcement is fitted to end portions of the plurality of first-impeller blades 11 on the air inlet 6 side.
  • An outer peripheral ring 15 has a shape covering outer peripheral sides of the first-impeller blades 11, and hence an outer diameter of the outer peripheral ring 15 is larger than an outer diameter of the first-impeller blades 11.
  • the second impeller 3b is arranged in an internal space (radially inner space) of the first impeller 3a having a cylindrical shape so as to be positioned between the main plate 10 of the first impeller 3a and the air inlet 6. Further, the second impeller 3b is supported by the motor shaft 9.
  • the second impeller 3b includes an annular hub 13, a plurality of second-impeller blades 14, and the outer peripheral ring 15.
  • the hub 13 is fixed in the vicinity of a distal end of the motor shaft 9.
  • the plurality of second-impeller blades 14 extend radially from the rotation axis 5, more specifically, are arranged radially on an outer periphery of the hub 13.
  • the outer peripheral ring 15 is arranged so as to connect together radially outer sides of the plurality of second-impeller blades 14.
  • a shape of each second-impeller blade 14 is changed from an inner peripheral side to an outer peripheral side.
  • the blade shape varying between the inner peripheral side and the outer peripheral side, a swirling-direction component c2 ⁇ of an outlet absolute flow, which is generated in a wake of the second-impeller blade 14 on the outer peripheral side (see FIG. 3 described later), is reduced.
  • a stagger angle ⁇ in a region of the second-impeller blade 14 on the outer peripheral side is set larger than a stagger angle in a region thereof on the inner peripheral side.
  • FIG. 3 is a sectional view for illustrating a shape of a part of the second-impeller blade 14 on the outer peripheral side, specifically, for illustrating an arc cross section having the rotation axis 5 as the center, which is developed into a plane. Further, FIG. 3 corresponds to a cross section of FIG. 1 at the position indicated by the reference symbol III.
  • the left side [case A] of FIG. 3 corresponds to a case where the stagger angle ⁇ on the outer peripheral side is set to be equal to that on the inner peripheral side
  • the right side [case B] of FIG. 3 corresponds to a case where the stagger angle ⁇ on the outer peripheral side is set larger than that on the inner peripheral side. That is, the first embodiment corresponds to the [case B].
  • An upper side in the drawing sheet of FIG. 3 corresponds to the air inlet 6 side, and a lower side in the drawing sheet of FIG. 3 corresponds to the main plate 10 side.
  • a direction from the right side to the left side in the drawing sheet corresponds to a rotation direction of the impeller 3.
  • an end portion in the rotation direction is referred to as a leading edge 16, and an end portion in a counter-rotation direction is referred to as a trailing edge 17.
  • a straight line connecting the leading edge 16 and the trailing edge 17 is referred to as a chord line 18.
  • An angle formed by a straight line 19 parallel to the rotation axis 5 and the chord line 18 is referred to as the stagger angle ⁇ .
  • the arrows illustrated on the lower side with respect to the trailing edge 17 in the drawing sheet form speed triangles for schematically illustrating a speed component of the flow on the downstream of the blade for the axial-flow fan.
  • An outlet peripheral speed u2 is proportional to a distance from the rotation axis 5.
  • the peripheral speed is higher on the outer peripheral side than the inner peripheral side, and the swirling-direction component c2 ⁇ of an outlet absolute speed c2 is larger on the outer peripheral side.
  • an outflow angle ⁇ 2 formed by an outlet relative speed w2 is increased, thereby being capable of reducing the swirling-direction component of the absolute speed.
  • the multiblade blower 1 when the drive motor 4 is operated, the first-impeller blades 11 and the second-impeller blades 14 are rotated through intermediation of the motor shaft 9, the main plate 10, and the hub 13. With this, outside air is sucked into the impeller 3 through the air inlet 6, and is blown into the casing 2 due to an effect of pressure rise by the impeller 3. Then, the outside air is reduced in speed by the enlarging air duct formed by the scroll wall 7 of the casing 2, and is recovered to be moved only by static pressure, to thereby be blown out to the outside through the air outlet 8. In this manner, the air is blown.
  • the multiblade blower 1 of the first embodiment includes the second impeller 3b of the axial-flow type inside the first impeller 3a, and hence performance of sending the outside air from the air inlet 6 to the main plate 10 side is high.
  • the air can be supplied to a region of each first-impeller blade 11 in the vicinity of the main plate 10.
  • the broken-line arrows of FIG. 4 schematically indicate a flow along a meridian plane from the air inlet 6 to the first-impeller blades 11.
  • the air passing through the outer peripheral sides of the second-impeller blades 14 flows into portions of the first-impeller blades 11 in regions closer to the second-impeller blades 14.
  • the multiblade blower 1 of the first embodiment is constructed such that the stagger angle ⁇ in the region of each second-impeller blade 14 on the outer peripheral side is set larger than the stagger angle in the region thereof on the inner peripheral side so as to reduce the swirling-direction component c2 ⁇ of the wake.
  • change in angle of the flow into the first-impeller blade 11 is suppressed to be small. Therefore, reduction of air-sending performance, which may be caused when the flow enters the first-impeller blade 11 at an improper angle, is reduced.
  • the large flow rate is secured, thereby being capable of providing the multiblade blower 1 reduced in noise.
  • An outer diameter of the first impeller 3a is represented by D1
  • a dimension of the impeller 3 in the rotation axis 5 direction is represented by L1
  • a distance in the first impeller 3a from an end portion on the air inlet 6 side to a position connected to the second impeller 3b is represented by L2
  • a distance in the first impeller 3a from the position connected to the second impeller 3b to a position connected to the main plate 10 is represented by L3.
  • the dimension in the rotation axis direction of the related-art general multiblade blower without the second impeller 3b is appropriately set up to about 0.5 time as large as D1.
  • the pressure increasing performance by the second impeller 3b is exerted.
  • the distance L2 in the first impeller 3a from the end portion on the air inlet 6 side to the position connected to the second impeller 3b is appropriately set up to about 0.5 time to about 1.0 time as large as D1.
  • the distance in the first impeller 3a from the position connected to the second impeller 3b to the position connected to the main plate 10 is appropriately set up to about 0.5 time as large as D1.
  • the dimension L1 of the impeller in the rotation axis direction is appropriately set to about 1.0 time to about 1.5 times as large as D1.
  • the dimension of the impeller 3 in the rotation axis 5 direction in the multiblade blower 1 can be increased.
  • the dimension in the rotation axis direction is increased, there is a problem in that runout of the impeller during the rotation is liable to be significant due to centrifugal forces generated in the blades during the rotation, displacement between the center of gravity of the impeller and the rotation axis, and the like.
  • at least a plurality of (as one preferred example, in the first embodiment, all of) the second-impeller blades 14 connect together the motor shaft 9 and the first-impeller blades 11.
  • the first-impeller blades 11 can be held not only by the main plate 10 but also by the second impeller 3b at a distance from the main plate 10.
  • the second impeller 3b contributing to the increase in the flow rate and the reduction of noise also contributes to the support of the first impeller 3a, thereby being capable of obtaining an advantage against the above-mentioned problem in that the runout during the rotation can be suppressed to be small.
  • FIG. 6 and FIG. 7 are views similar to FIG. 1 and FIG. 3 , for illustrating the second embodiment. That is, FIG. 6 is an external view of a multiblade blower of the second embodiment when viewed from the same direction as FIG. 1 , and FIG. 7 corresponds to a cross section of FIG. 6 at the position indicated by the reference symbol VII. Further, the second embodiment is different from the first embodiment in the shape of each second-impeller blade, and except for the parts described below, the second embodiment is similar to the first embodiment.
  • a shape of each second-impeller blade 114 is changed, that is, a chord line LB in a region of each second-impeller blade 114 on the outer peripheral side is set smaller than a chord line in a region thereof on the inner peripheral side.
  • FIG. 7 is an illustration of a [case C] where the chord line LB on the outer peripheral side is set equal to that on the inner peripheral side, and a [case D] where the chord line LB on the outer peripheral side is set smaller than that on the inner peripheral side.
  • the [case D] corresponds to the second embodiment.
  • the arrows illustrated on the lower side with respect to the trailing edge 17 in the drawing sheet form speed triangles for schematically illustrating a speed component of a flow on the downstream of the blade for the axial-flow fan, and also illustrate an inlet relative speed w1 in an overlapping manner.
  • Change in angle from the inlet relative speed w1 to the outlet relative speed w2 corresponds to a deflection angle ⁇ .
  • the deflection angle ⁇ is increased.
  • the swirling-direction component c2 ⁇ of the outlet absolute flow is also increased.
  • the multiblade blower 101 of the second embodiment is constructed such that the swirling-direction component of the wake of the region of each second-impeller blade 114 on the outer peripheral side is reduced.
  • the change in angle of the flow into the first-impeller blade 11 is suppressed to be small. Therefore, the reduction of the air-sending performance, which may be caused when the flow enters the first-impeller blade 11 at an improper angle, is reduced.
  • the large flow rate is secured, thereby being capable of providing the multiblade blower 101 reduced in noise.
  • FIG. 8 is a view similar to FIG. 1 , for illustrating the third embodiment.
  • FIG. 8 is an external view of a multiblade blower of the third embodiment when viewed from the same direction as FIG. 1 . Further, except for the parts described below, the third embodiment is similar to the first embodiment or the second embodiment.
  • the number of the second-impeller blades present therein varies between a region on the outer peripheral side and a region on the inner peripheral side. That is, as an example, as illustrated in FIG. 8 , five second-impeller blades 214a are arranged in total in the region on the outer peripheral side (region in a substantially annular shape in FIG. 8 ), and ten second-impeller blades 214a and 214b are arranged in total in the region on the inner peripheral side (region in a substantially circular shape in FIG. 8 ).
  • the number of the second-impeller blades arranged in the region on the outer peripheral side is set smaller than the number of the second-impeller blades arranged in the region on the inner peripheral side.
  • the number in each of the regions is merely an example, and the present invention is not limited thereto.
  • each second-impeller blade 214a has a relatively large dimension in the radial direction, and an end portion of each second-impeller blade 214a on the radially outer side reaches the first impeller 3a.
  • each second-impeller blade 214b has a relatively small dimension in the radial direction, and an end portion of each second-impeller blade 214b on the radially outer side is away from the first impeller 3a as a free end.
  • those two types of the second-impeller blades 214a and the second-impeller blades 214b are arrayed equiangularly and alternately.
  • the energy applied by the blades of the second impeller 3b to the air is reduced.
  • the deflection angle ⁇ of the flow is reduced, and the swirling-direction component c2 ⁇ to be applied is also reduced.
  • the air passing through the region of each second-impeller blade 214a on the outer peripheral side flows into a region of each first-impeller blade 11 in the vicinity of the second-impeller blade 214a.
  • the multiblade blower 201 of the third embodiment is constructed such that the swirling-direction component of the wake of the region of each second-impeller blade 214a on the outer peripheral side is reduced.
  • the change in angle of the flow into the first-impeller blade 11 is suppressed to be small. Therefore, the reduction of the air-sending performance, which may be caused when the flow enters the blade at an improper angle, is reduced.
  • the large flow rate is secured, thereby being capable of providing the multiblade blower 1 reduced in noise.
  • FIG. 9 and FIG. 10 are views for illustrating a blade shape of each first-impeller blade according to the reference example. More specifically, FIG. 9 and FIG. 10 are cross sections of the first-impeller blade respectively taken along the arrow IX and the arrow X of FIG. 2 .
  • each first-impeller blade 11 of the first impeller 3a varies between a region on the upstream side with respect to the second impeller 3b (illustrated in FIG. 9 ) and a region on the downstream side with respect to the second impeller 3b (illustrated in FIG. 10 ).
  • each first-impeller blade 311 on an inlet side is referred to as a leading edge 320.
  • reference symbol 321 represents a straight line passing through the rotation axis 5 and the leading edge 320 and reference symbol 322 represents a straight line crossing the straight line 321 at a right angle at the leading edge 320 and extending toward a rearward side in a rotation direction 317
  • an angle formed by a tangent line 323 of the leading edge 320 and the above-mentioned straight line 322 is referred to as a blade inlet angle ⁇ b1.
  • an inlet angle ⁇ b1 in a region of the first-impeller blade 311 on the downstream side with respect to the second impeller 3b is set larger than an inlet angle ⁇ b1 in a region of the first-impeller blade 311 on the upstream side with respect to the second impeller 3b (illustrated in FIG. 9 ).
  • FIG. 9 and FIG. 10 which are illustrated on the lower side (rotation axis side) with respect to the leading edges 320 in the blade cross section, form speed triangles for illustrating a state of the flow on the inlet side.
  • a swirling-direction component c1 ⁇ of an absolute flow c1 flowing into the first-impeller blade 311, which is parallel to an inlet peripheral speed u1 is larger than a swirling-direction component c2 ⁇ of an absolute flow c1 flowing into the first-impeller blade 311 in the region of the first-impeller blade 311 on the upstream side with respect to the second impeller 3b.
  • a relative flow w1 flowing into the first-impeller blade 311 also varies between the region on the upstream side and the region on the downstream side. In the region on the downstream side with respect to the second impeller 3b, the flow enters the first-impeller blade 311 at a small inflow angle ⁇ 1.
  • the inlet angle ⁇ b1 in the region of the first-impeller blade 311 on the downstream side with respect to the second impeller 3b is set larger than the inlet angle ⁇ b1 in the region of the first-impeller blade 311 on the upstream side with respect to the second impeller 3b.

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Claims (6)

  1. Soufflante à aubes multiples (1, 101, 201) comprenant :
    un carter (2) ayant une entrée d'air (6) ;
    une première roue (3a) disposée dans le carter de manière à pouvoir tourner ; et
    une seconde roue (3b) agencée dans un espace interne de la première roue (3a) de manière à pouvoir tourner,
    la première roue (3a) comprenant un ventilateur centrifuge comprenant une pluralité d'aubes de première roue (11, 311) positionnées de manière à former une forme cylindrique,
    la seconde roue (3b) comprenant un ventilateur à écoulement axial comprenant une pluralité d'aubes de seconde roue (14, 114, 214a, 214b) s'étendant radialement à partir d'un axe de rotation,
    caractérisée en ce que :
    un angle de décalage dans une zone de chacune des aubes de seconde roue (14) sur le côté périphérique externe est réglé pour être plus grand qu'un angle de décalage dans une zone de chacune des aubes de seconde roue (14) sur le côté périphérique interne de telle sorte qu'une composante de direction de tourbillonnement d'un sillage dans une zone sur un côté périphérique externe dans l'espace interne de la première roue (3a) est plus petite qu'une composante de direction de tourbillonnement d'un sillage dans une région sur un côté périphérique interne dans l'espace interne.
  2. Soufflante à aubes multiples (1, 101, 201) comprenant :
    un carter (2) ayant une entrée d'air (6) ;
    une première roue (3a) disposée dans le carter de manière à pouvoir tourner ; et
    une seconde roue (3b) agencée dans un espace interne de la première roue (3a) de manière à pouvoir tourner,
    la première roue (3a) comprenant un ventilateur centrifuge comprenant une pluralité d'aubes de première roue (11, 311) positionnées de manière à former une forme cylindrique,
    la seconde roue (3b) comprenant un ventilateur à écoulement axial comprenant une pluralité d'aubes de seconde roue (14, 114, 214a, 214b) s'étendant radialement à partir d'un axe de rotation,
    caractérisée en ce que :
    une ligne de corde dans la zone de chacune des aubes de seconde roue (114) sur le côté périphérique externe est établie pour être plus petite qu'une ligne de corde dans la région de chacune des aubes de seconde roue (114) sur le côté périphérique interne de telle sorte qu'une composante de direction de tourbillonnement d'un sillage dans une zone sur un côté périphérique externe dans l'espace interne de la première roue (3a) est plus petite qu'une composante de direction de tourbillonnement d'un sillage dans une région sur un côté périphérique interne dans l'espace interne.
  3. Soufflante à aubes multiples (1, 101, 201) comprenant :
    un carter (2) ayant une entrée d'air (6) ;
    une première roue (3a) disposée dans le carter de manière à pouvoir tourner ; et
    une seconde roue (3b) agencée dans un espace interne de la première roue (3a) de manière à pouvoir tourner,
    la première roue (3a) comprenant un ventilateur centrifuge comprenant une pluralité d'aubes de première roue (11, 311) positionnées de manière à former une forme cylindrique,
    la seconde roue (3b) comprenant un ventilateur à écoulement axial comprenant un certain nombre d'aubes de seconde roue (214a) agencées dans la zone du côté périphérique extérieur dans l'espace interne de la première roue (11, 311), et un certain nombre de pales de deuxième roue (214a, 214b) disposées dans la zone du côté périphérique interne dans l'espace interne,
    dans laquelle les aubes de seconde roue s'étendent radialement à partir d'un axe de rotation,
    caractérisée en ce que :
    le nombre d'aubes de seconde roue (214a) agencées dans la zone du côté périphérique externe dans l'espace interne de la première roue (11, 311) est réglé pour être plus petit que le nombre d'aubes de seconde roue (214a, 214b) agencées dans la zone du côté périphérique interne dans l'espace interne de sorte qu'une composante de direction de tourbillonnement d'un sillage dans une zone sur un côté périphérique externe dans l'espace interne de la première roue (3a) est plus petite qu'une composante de direction de tourbillonnement d'un sillage dans une zone sur un côté périphérique interne dans l'espace interne.
  4. Soufflante à aubes multiples (1, 101, 201) selon l'une quelconque des revendications 1 à 3,
    dans lequel la première roue (3a) comprend une plaque principale (10) fixée à un arbre d'entraînement (9),
    dans lequel la pluralité d'aubes de première roue (11, 311) sont disposées le long d'une périphérie de la plaque principale (10),
    dans lequel la pluralité d'aubes de seconde roue (14, 114, 214a, 214b) relie ensemble l'arbre d'entraînement (9) et les aubes de première roue (11, 311), et
    dans lequel la pluralité d'aubes de première roue (11, 311) sont supportées par la plaque principale (10) et sont également supportées par les aubes de seconde roue (14, 114, 214a).
  5. Soufflante à aubes multiples (1, 101, 201) selon l'une quelconque des revendications 1 à 4, dans laquelle une distance dans la première roue (3a) à partir d'une partie d'extrémité du côté d'entrée d'air vers une position reliée à la seconde roue (3b) est de 0,5 fois à 1,0 fois aussi grande qu'un diamètre extérieur de la première roue (3a) .
  6. Soufflante à aubes multiples (1, 101, 201) selon la revendication 5, dans laquelle une dimension de la première roue (3a) dans une direction d'axe de rotation est de 1,0 fois à 1,5 fois aussi grande que le diamètre extérieur de la première roue (3a).
EP13889351.6A 2013-07-10 2013-07-10 Ventilateur à pales multiples Active EP3020979B1 (fr)

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PCT/JP2013/068871 WO2015004750A1 (fr) 2013-07-10 2013-07-10 Ventilateur à pale multiples

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Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH08135596A (ja) * 1994-11-10 1996-05-28 Daikin Ind Ltd 遠心送風機用羽根車

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DE2150439A1 (de) * 1971-10-09 1973-04-12 Sueddeutsche Metallwerke Gmbh Geblaese
JPS62206291A (ja) * 1986-03-05 1987-09-10 Sanyo Electric Co Ltd 送風装置
JPH06129388A (ja) * 1992-10-16 1994-05-10 Matsushita Seiko Co Ltd 送風機
JPH10141296A (ja) * 1996-11-12 1998-05-26 Kubota Corp 送風機
US6345956B1 (en) * 1998-07-14 2002-02-12 Delta Electronics, Inc. Impeller of a blower having air-guiding ribs with geometrical configurations
JP3507758B2 (ja) * 2000-03-27 2004-03-15 松下エコシステムズ株式会社 多翼ファン
JP2007231863A (ja) 2006-03-02 2007-09-13 Toshiaki Nakayama 羽根車の保持リングを軸流ファン構造とするシロッコファン

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH08135596A (ja) * 1994-11-10 1996-05-28 Daikin Ind Ltd 遠心送風機用羽根車

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EP3020979A4 (fr) 2017-03-01
WO2015004750A1 (fr) 2015-01-15
JP6038320B2 (ja) 2016-12-07
JPWO2015004750A1 (ja) 2017-02-23
EP3020979A1 (fr) 2016-05-18

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