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
  • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
  • F04D29/68—Combating cavitation, whirls, noise, vibration or the like; Balancing by influencing boundary layers
  • F04D29/681—Combating cavitation, whirls, noise, vibration or the like; Balancing by influencing boundary layers especially adapted for elastic fluid pumps
• • 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
  • F04D29/283—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 rotors of the squirrel-cage 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
  • F04D29/00—Details, component parts, or accessories
  • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
  • F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps
  • F04D29/667—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps by influencing the flow pattern, e.g. suppression of turbulence

Definitions

• the present invention relates to a centrifugal blower impeller and a centrifugal blower provided with the same, and more particularly, to a centrifugal blower impeller in which ends of a plurality of blades extending from a main plate are connected by an annular side plate, and a centrifugal blower provided with the impeller.
• FIG. 1 shows a side view of a conventional multi-blade fan
• FIG. 2 shows a perspective view of an impeller of the conventional multi-blade fan
• FIG. 3 shows a conventional multi-blade fan.
• FIG. 3 shows a plan view of the impeller.
• the multi-blade blower 10 includes an impeller 13, a casing 11 for covering the impeller 13, a motor 14 for rotating the impeller 13, and the like.
• the impeller 13 one end of a number of blades 33 is fixed to an outer peripheral edge of a disk-shaped main plate 31, and the other ends of the blades 33 are connected by an annular side plate 32.
• the casing 11 has a gas outlet 11 a and a gas inlet 11 b surrounded by a bell mouth 12.
• the suction port 11b faces the side plate 32 of the impeller 13.
• the outlet 11a is formed in a direction perpendicular to the inlet 11b so as to blow out gas in a direction substantially perpendicular to the rotation axis 0-0 of the impeller 13.
• each blade 33 of the impeller 13 pumps out gas from the space on the inner circumference side to the space on the outer circumference side, and gas flows from the suction port 11 b into the space on the inner circumference side of the impeller 13. While being sucked, the gas pushed to the outer peripheral side of the impeller 13 is sent out through the outlet 11a. That is, the multi-blade blower 10 sucks gas from the suction port 11b and sends out gas from the outlet 11a. In such a multi-blade blower 10, there is noise due to turbulent vortices generated near the main plate 31.
• the gas sucked from the inlet 11 b flows mainly from the direction toward the main plate 31 toward the outer periphery gradually as shown in FIG. 1 (a). Yes (see gas flow W).
• a part of the gas sucked from the suction port 11b flows toward the outer periphery after colliding with the main plate 31 near the main plate 31.
• Yes see gas flow X.
• a turbulent vortex is generated due to collision with the main plate 31.
• This turbulent vortex causes the gas flow X to move toward the outer periphery, and the flow colliding with the main plate 31 further joins.
• the turbulent vortex of the gas flow X gradually develops and forms the largest turbulent vortex at the inner peripheral edge of the wing 33.
• the developed turbulent vortex is ejected toward the outer peripheral side by the wings 33 to generate noise.
• a swirling vortex having a vortex center near the outer peripheral end of the side plate 32 is generated.
• This swirling vortex does not contribute to the air blowing work of the impeller 13, and as a result, causes a reduction in fan efficiency and noise. Specifically, it is caused by the following generation mechanism.
• a ratio b / B of the axial length b of the portion where the swirl vortex Y is generated to the axial total length B of the impeller 13 (hereinafter referred to as a blockage factor BF ).
• the blast work has not been done effectively. This results in reduced fan efficiency and noise.
• Multi-blade blowers used in air conditioners are required to further reduce noise.
• noise caused by turbulent vortices near the main plate is generated not only by multi-blade fans but also by centrifugal fans including turbo fans.
• An object of the present invention is to provide an impeller capable of reducing noise and to provide a low-noise centrifugal blower.
• An impeller of a centrifugal blower includes a main plate that rotates around a rotation axis, a plurality of blades that are annularly arranged around the rotation shaft and one ends of which are fixed to the main plate, respectively.
• An annular side plate connecting the other ends.
• An irregular corrugated shape is formed at least near the inner peripheral edge of the plurality of blades on the side surface of the main plate on the side plate side.
• the corrugated shape is formed at least on the side of the main plate on the side of the side plate near the inner peripheral edge of the blade.
• the turbulent vortex develops from the inner peripheral side to the outer peripheral side of the main plate, it is most effective to reduce the turbulent vortex immediately before being ejected by the wings. It must be installed at least near the inner edge of the wing on the side of the main plate on the side plate side. Furthermore, in order to prevent the turbulent vortex that has been collapsed and reduced by the corrugated shape from developing again, the corrugated shape is within the range of the radial length of the blade from the inner peripheral edge to the inner peripheral side of the blade. It is desirable to be installed inside.
• the wave shape may be installed not only near the inner peripheral edge of the wing, but also near the rotation axis. Thereby, the turbulent vortex generated each time the gas flow collides with the main plate can be reduced.
• An impeller for a centrifugal blower includes a main plate that rotates about a rotation axis, a plurality of blades that are arranged in a ring around the rotation axis, and one end of each of which is fixed to the main plate, and a plurality of blades. And an annular side plate connecting the other ends of the two. An uneven corrugated shape is formed on the surface of the side plate on the main plate side.
• the corrugated shape of the concavo-convex shape is formed on the surface of the side plate on the main plate side, so that pressure fluctuation near the impeller outlet of the side plate is reduced. Then, the gas flow discharged to the outlet side by the impeller becomes difficult to be sucked into the inner peripheral side of the impeller again from the side plate side in the rotation axis direction of the impeller, so that the gas flow was generated in the vicinity of the side plate. The swirling vortex becomes smaller. As a result, the portion of the re-impeller with a small BF value that can effectively perform the blowing work becomes larger, so that the efficiency of the blower is improved and the noise is reduced.
• the impeller of a centrifugal blower according to claim 3 is the impeller according to claim 1 or 2, wherein the waveform is a triangular wave.
• the impeller of a centrifugal blower according to claim 4 is the impeller according to claim 1 or 2, wherein the waveform is sinusoidal.
• the impeller of a centrifugal blower according to claim 5 is the impeller according to claim 1 or 2, wherein the waveform is a rectangular wave.
• the impeller of a centrifugal blower according to claim 6 is the impeller according to any one of claims 1 to 5, wherein the waveform has a wave pitch of 2 mm or more and 8 mm or less, and a wave height of 1 mm or more and 5 mm or more. mm or less.
• a centrifugal blower is characterized in that the impeller according to any one of claims 1 to 6, a driving unit for rotating the main plate, a suction port and an impeller opposed to an opening on the inner peripheral side of the side plate. And a casing provided on the outer peripheral side and having an air outlet for sending out gas in a direction substantially perpendicular to the rotation axis and covering the impeller.
• centrifugal blower when the main plate is rotated by the driving means, the impeller rotates for casing. Then, each blade of the impeller blows out gas from the space on the inner circumference side to the space on the outer circumference side, and the gas pushed out from the suction port to the outer circumference side of the impeller is sent out through the outlet. In other words, the centrifugal blower sucks gas from the inlet and sends out gas from the outlet.
• the corrugated shape formed on the main plate allows the gas flow to collide with the main plate and to merge with the flow.
• the resulting turbulent vortex is crushed and reduced.
• noise generated when gas is exhausted by the impeller can be reduced.
• the swirling vortex generated near the side plate is reduced by the corrugated shape formed on the side plate.
• the part of the re-impeller with a small BF value that can effectively perform the blowing work becomes larger, so that the efficiency of the blower is improved and the noise is reduced.
• FIG. 1 (a) is a side view of a conventional multi-blade blower (the casing is a sectional view).
• FIG. 1 (b) is a side view of a conventional multi-blade blower, illustrating a noise generation mechanism in the vicinity of a main plate (partially showing a cross section of an impeller).
• FIG. 1 (c) is a side view of a conventional multi-blade blower, illustrating a noise generation mechanism near a side plate (partially showing a cross section of an impeller).
• FIG. 2 is a perspective view of an impeller of a conventional multi-blade fan.
• FIG. 3 is a plan view of an impeller of a conventional multi-blade fan.
• FIG. 4 is a side view of the multi-blade blower of the first embodiment (a casing is a sectional view).
• FIG. 5 is a side view (partially sectioned) of the impeller of the multi-blade fan of the first embodiment.
• FIG. 6 is a plan view of an impeller of the multi-blade blower according to the first embodiment.
• Fig. 7 (a) is an enlarged view of the waveform shape (triangular wave shape).
• Fig. 7 (b) is an enlarged view of the waveform (sinusoidal).
• Fig. 7 (c) is an enlarged view of the waveform (rectangular waveform).
• FIG. 8 (a) is a side view of the multi-blade blower of the first embodiment, illustrating a noise reduction effect of a corrugated shape formed on a main plate (a part of the cross section of the impeller is shown).
• FIG. 8 (b) is a side view of the multi-blade blower of the first embodiment, illustrating the noise reduction effect of the corrugated shape formed on the side plate.
• FIG. 8 (c) is a side view of the multi-blade blower of the first embodiment, illustrating the noise reduction effect of the cut-out shape of the main plate between the blades (partially showing a cross section of the impeller).
• FIG. 9 is a plan sectional view of an impeller of a tarpo fan according to a second embodiment.
• a multi-blade blower (centrifugal blower) according to an embodiment of the present invention includes an impeller 13 of a conventional multi-blade blower 10 shown in FIGS. It has a corrugated shape in the vicinity of the edge, a corrugated shape on the side of the main plate 31 of the side plate 32, and a cutout at the front in the rotation direction of the plurality of interblades 35 of the main plate 31. The only difference is that it has a curved shape.
• FIG. 4 shows a side view of the multi-blade blower 40 of the present embodiment
• FIGS. 5 and 6 show a side view and a plan view of the impeller 43 of the multi-blade blower 40.
• the multi-blade blower 40 is mainly composed of an impeller 63, a casing 11 for covering the impeller 63, and a motor 14 for rotating the impeller 43.
• the impeller 43 has a plurality of blades 33 fixed to an outer peripheral edge of a disk-shaped main plate 61, and the other ends of the plurality of blades 33 are connected by an annular side plate 62. Details of the impeller 43 will be described later.
• the casing 11 has a gas outlet 11 a and a gas inlet 11 b surrounded by a bell mouth 12.
• the suction port 11b is arranged to face the side plate 62 of the impeller 43.
• the gas flowing through the suction port 1 1b into the space around the inner periphery of the impeller 4 3 generally flows along the rotation axis 0-0 of the impeller 43, and the rotation of the impeller 43 As a result, the fluid flows in a direction away from the rotation axis 0-0 (in the outer circumferential direction of the impeller 43).
• the outlet 11 a is formed so as to blow out gas in a direction substantially orthogonal to the rotation axis 0-0 of the impeller 43 and so as to be orthogonal to the inlet 11 b.
• the rotary shaft of the motor 14 is mounted in the center hole 61 a of the main plate 61 (see FIG. 6), and the entire impeller 43 is rotated by rotating the main plate 61.
• the main body of the motor 14 is fixed to the casing 11.
• the impeller 43 includes a main plate 61, a plurality of blades 33, and an annular side plate 62, as shown in FIGS.
• the impeller 43 is a resin product in which the main plate 61, the plurality of blades 33, and the side plates 62 are all integrally formed using a mold.
• the main plate 61 is a disk-shaped member having a center hole 61a formed therein.
• the rotary shaft of the motor 14 is fixed to the center hole 61a.
• the waveform shape 64 has a triangular wave shape, and has a wave pitch P of 3 mm and a wave height H of 2 mm (see FIG. 7 (a)).
• the waveform shape is not limited to a triangular wave shape, but may be a sine wave shape or a rectangular wave shape as shown in FIGS. 7 (b) and 7 (G).
• the dimensions of the waveform shape are not limited to the dimensions of the present embodiment, and the pitch P is in the range of 2 mm or more and 8 mm or less, and the wave height H is 1 mm or more and 5 mm or less. It only has to be within the range.
• the interblade portion 65 located between the plurality of wings 33 of the main plate 61 is notched forward in the rotation direction.
• These inter-blade portions 65 are circumferentially thicker than the circumferential thickness of the wing 33 and do not reach the rotational direction rearward of the other adjacent wings 33 in the rotational direction. Cut out in length.
• the radial direction of the interblade portion 65 is notched along the shape of the blade 33 so as to extend from the outer peripheral edge to the inner peripheral edge.
• the wing 33 is a member having a concave shape in the front in the rotation direction and arranged in a plurality of rings around the rotation axis 0-0.
• One end of the wing 33 is fixed to the outer peripheral edge of the main plate 61, and extends therefrom without any twist along the rotation axis 0-0.
• the other ends of the wings 33 are connected by an annular side plate 62 as shown in FIGS.
• the annular side plate 62 is arranged on the outer peripheral side of the other end of the wing 33, and connects the wings 33.
• the side plate 62 is also integrally formed with the main plate 61 and the plurality of blades 33.
• An uneven corrugated shape 66 is formed on the surface of the side plate 62 on the main plate 61 side.
• the waveform shape 66 is, like the waveform shape 64 of the main plate 61, a triangular waveform having a wave pitch P of 3 mm and a wave height H of 2 mm (see FIG. 7 (a)).
• the waveform shape is not limited to a triangular wave shape, but may be a sine wave shape or a rectangular wave shape as shown in FIGS. 7 (b) and 7 (c).
• the dimensions of the waveform shape are not limited to the dimensions of the present embodiment, and the pitch P is in the range of 2 mm or more and 8 mm or less, and the wave height H is in the range of 1 mm or more and 5 mm or less. Should be fine.
• the multi-blade blower 40 sucks gas from the inlet 11b along the rotation axis 0-0, and sends out gas from the outlet 11a in a direction perpendicular to the rotation axis 0-0.
• FIG. 4 shows only the gas flow Z on the right side of the rotation axis 0-0, the gas discharged to the outer peripheral side of the impeller 13 on the left side of the rotation axis 0-0 is It flows up to the outlet 1 1a for one thing 1 1 and is blown out from there.
• the inter-blade portion 65 of the main plate 61 of the impeller 43 of the present embodiment is, as described above, circumferentially larger than the circumferential thickness of the blade 33, and radially.
• Each of the blades 33 is notched to a length that extends from the outer peripheral edge to the inner peripheral edge of the blade 33 along the shape of the blade. Using this shape, the two impellers 43 are overlapped from the rotation axis 0-0 direction.
• the corresponding blades 33 of the other impeller 43 can be fitted into the cutouts of the plurality of blade portions 65 of one impeller 43.
• the two impellers 43 fitted in this way are further transported after being loaded to a predetermined loading height.
• the noise value was reduced by 0.8 dB compared to the conventional example.
• the noise value was reduced by 0.5 dB compared to the conventional example.
• the noise value was reduced by 0.5 dB compared to the conventional example.
• the features of the multi-blade blower of the present embodiment include the following.
• the corrugated shape 64 of the concavo-convex shape is formed at least in the vicinity of the inner peripheral edge of the blade 33 on the side of the side plate 62 of the main plate 61.
• the turbulent vortex developed due to the collision of the gas flow Z1 with the main plate 61 and the merging of the flows is collapsed just before reaching the wings 33, as shown in Fig. 8 (a). It becomes smaller.
• noise generated when the gas flow Z1 is extracted by the wings 33 can be reduced. 2 Noise reduction by the corrugated shape formed on the side plate of the impeller
• a swirling vortex having a vortex center near the outer peripheral end of the side plate 32 is generated.
• This swirling vortex does not contribute to the air blowing work of the impeller 13 and, as a result, lowers the fan efficiency and causes noise. Specifically, it is caused by the following generation mechanism.
• a part of the gas in the casing 11 is discharged to the outer periphery of the impeller 13 near the side plate 32, and then the bell mouth of the impeller 13 is formed.
• a swirling vortex Y is generated from near 1 2 to the inner circumference side of the impeller 13 again. Therefore, in the impeller 13, the ratio b ZB (hereinafter referred to as a blockage factor BF ) of the axial length b of the portion where the swirl vortex Y is generated with respect to the axial total length B of the impeller 13 is given.
• the ventilation work has not been effectively performed. This results in reduced fan efficiency and noise.
• the impeller 43 of the multi-blade blower 40 of the present embodiment since the corrugated shape 66 of the uneven shape is formed on the surface of the side plate 62 on the main plate 61 side, the impeller 4 of the side plate 62 is formed. (3) Pressure fluctuation near the outlet is reduced. Then, as shown in FIG. 8 (b), the gas flow discharged to the outlet side by the impeller 43 changes from the rotation axis side plate 62 side of the impeller 43 to the inner periphery of the impeller 43 again. Since it is difficult to be sucked into the side, the swirl vortex Z 2 generated near the side plate 62 is reduced. Thus, since the effective portion, which can blow job B F values b 1 ZB 1 small Sakunari impeller 4 3 increases, increased blower efficiency is, noise is also reduced.
• the impeller 43 of the multi-blade blower 40 In the impeller 43 of the multi-blade blower 40 according to the present embodiment, at least the front in the rotation direction of the inter-blade portion 65 located between the plurality of blades 33 of the main plate 61 is notched.
• the turbulent vortex developed by the collision of the gas flow Z 3 with the main plate 61 and the merge of the flow is the inter-blade 6 5 cut out just before being blown out by the wing 33.
• a part of the main plate 61 is released outward from the main plate 61 in the axial direction.
• the noise generated when the gas flow is forced out by the wings 33 can be reduced.
• the blade portion 65 of the impeller 43 of the present embodiment has a circular shape in the rotation direction front of the main plate 61. It is partially notched in the circumferential direction, and is not cut to the rear in the rotation direction of the interblade 65. Therefore, there is no increase in gas flow separation behind the interblade 65 in the rotational direction. As a result, the effect of noise reduction by notching the front portion in the rotation direction of the blade portion 65 is not impaired.
• the inter-blade portion 65 of the impeller 43 of the present embodiment is cut out from the outer peripheral edge to the inner peripheral edge of the blade 33, so that the turbulent vortex of the gas flow Z3 is generated by the blade. Before reaching the outer peripheral edge of 33, it is easy to escape from the cut-out space 65. Thereby, the turbulent vortex reaching the outer peripheral edge of the wing 33 can be further reduced, and the noise can be reduced.
• the inter-blade portion 65 of the main plate 61 of the impeller 43 of the present embodiment has, in the circumferential direction, a thickness greater than the circumferential direction of the blade 33 and a radial direction. Is cut off so that the curvature of the wing 33 extends from the outer peripheral edge to the inner peripheral edge of the wing 33 along the rib shape.
• two impellers 43 can be overlapped from the rotation axis 0-0 direction, and the corresponding blades 33 can be fitted into the notches of the plurality of blade portions 65. Thereby, the loading efficiency when loading the impeller 43 can be improved.
• This embodiment is a case where the present invention is applied to an impeller of a turbo blower. That is, the waveform shape 64 formed on the main plate 61 of the multi-blade blower 40 of the embodiment is applied to the impeller 73 of the turbo blower.
• FIG. 9 shows a cross-sectional plan view of an impeller 73 of the turbo blower of the present embodiment.
• a plurality of blades 93 are fixed to an outer peripheral edge of a disk-shaped main plate 91, and the other ends of the plurality of blades 93 are connected by an annular shroud (side plate) not shown.
• a plurality of blades 93 are formed at equal intervals in the rotational direction, and near the inner peripheral edge of the plurality of blades 93, around the inner peripheral edge.
• a corrugated shape 94 is formed along the shape.
• the waveform shape 94 has a triangular wave shape, a sine wave shape or a rectangular wave shape as shown in FIGS. 7A to 7C as in the above-described embodiment, and the wave pitch P is 2
• the height of the wave is in the range of 1 mm to 5 mm.
• the corrugated shape 94 is formed at least on the shroud side surface of the main plate 91 at least near the inner peripheral edge of the wing 93, so that the gas flow
• the turbulent vortex developed by the collision with the main plate 91 and the merging of the flow is crushed just before it reaches the wings 93, and becomes smaller, reducing the noise generated when the wings 93 discharge the gas flow. Can be smaller.
• the present invention is applied to a centrifugal blower using a resin impeller, but the present invention can also be applied to a centrifugal blower using a sheet metal impeller.
• the noise in the impeller of the centrifugal blower can be reduced.

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• Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• General Engineering & Computer Science (AREA)
• Structures Of Non-Positive Displacement Pumps (AREA)

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Citations (6)

• 2002
  • 2002-06-12 ES ES02738677T patent/ES2387063T3/es not_active Expired - Lifetime
  • 2002-06-12 EP EP02738677A patent/EP1411248B8/de not_active Expired - Lifetime
  • 2002-06-12 WO PCT/JP2002/005882 patent/WO2003002873A1/ja active Application Filing
  • 2002-06-12 AT AT02738677T patent/ATE556226T1/de active
  • 2002-06-28 CN CN02240970U patent/CN2575343Y/zh not_active Expired - Lifetime
  • 2002-06-28 CN CN02141237.5A patent/CN1212479C/zh not_active Expired - Fee Related

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