WO2022085332A1 - 送風機 - Google Patents

送風機 Download PDF

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Publication number
WO2022085332A1
WO2022085332A1 PCT/JP2021/033321 JP2021033321W WO2022085332A1 WO 2022085332 A1 WO2022085332 A1 WO 2022085332A1 JP 2021033321 W JP2021033321 W JP 2021033321W WO 2022085332 A1 WO2022085332 A1 WO 2022085332A1
Authority
WO
WIPO (PCT)
Prior art keywords
shroud
flow path
intake nozzle
case
blower
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.)
Ceased
Application number
PCT/JP2021/033321
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
文也 石井
昇一 今東
修三 小田
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.)
Denso Corp
Original Assignee
Denso Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Denso Corp filed Critical Denso Corp
Publication of WO2022085332A1 publication Critical patent/WO2022085332A1/ja
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/08—Sealings
    • F04D29/16—Sealings between pressure and suction sides
    • F04D29/161—Sealings between pressure and suction sides especially adapted for elastic fluid pumps
    • F04D29/162—Sealings between pressure and suction sides especially adapted for elastic fluid pumps of a centrifugal flow wheel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/08—Sealings
    • F04D29/16—Sealings between pressure and suction sides
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/4206—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps
    • F04D29/4213—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps suction ports
    • 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
    • F04D29/44—Fluid-guiding means, e.g. diffusers
    • F04D29/441—Fluid-guiding means, e.g. diffusers especially adapted for elastic fluid pumps
    • F04D29/444—Bladed diffusers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2250/00—Geometry
    • F05D2250/50—Inlet or outlet
    • F05D2250/51—Inlet

Definitions

  • This disclosure relates to a blower.
  • a blower in which a centrifugal fan is arranged inside a case in which a bell mouth serving as an air suction port is formed is known.
  • the inner peripheral edge of the bell mouth is arranged radially inside the cylindrical portion of the shroud on the air suction port side of the centrifugal fan.
  • the blower is provided with an annular seal wall having a U-shaped cross section at a radial outer portion of the inner peripheral edge of the bell mouth. The seal wall covers the end of the shroud on the air suction port side with a predetermined gap.
  • the seal wall is for reducing the flow rate of a part of the air blown out from the air outlet of the centrifugal fan through the gap flow path formed in the gap between the shroud and the seal wall and flowing back to the front edge side of the blade again.
  • Patent Document 1 describes that by reducing the flow rate of the backflow air, the noise generated by the interference between the mainstream and the backflow air sucked into the fan from the bell mouth is reduced.
  • the backflow air blown from the gap flow path to the front edge side of the blade has a large velocity component in the rotation direction of the fan. Therefore, in this configuration, the crossing angle between the backflow air blown from the gap flow path to the front edge side of the wing and the mainstream sucked into the fan from the bell mouth is large, so the noise generated by the interference between the mainstream and the backflow air is sufficient. It is difficult to reduce to.
  • the blower comprises a case, a fan and an intake nozzle.
  • the case has a bell mouth that forms a suction port for sucking air.
  • the fan rotatably provided inside the case has a plurality of blades arranged around the axis, a shroud annular portion connected to a portion of the blade on the suction port side in the axial direction, and a diameter of the shroud annular portion. It has a shroud tubular portion that extends tubularly from a portion inside the direction toward the bellmouth side, and a main plate connected to a portion of the wing opposite to the shroud annular portion.
  • the intake nozzle is provided from the radial inner region of the bell mouth to the radial inner region of the shroud cylinder portion, and is formed in a tubular shape whose diameter gradually decreases from the bell mouth side toward the shroud cylinder portion side.
  • a first flow path formed between the intake nozzle and the bell mouth, a second flow path formed between the intake nozzle and the shroud cylinder portion, and a shroud cylinder portion, a shroud annular portion, and a case. It communicates with the gap flow path formed between the inner wall and the inner wall.
  • the intake nozzle has a shape that gradually reduces in diameter from the bell mouth side toward the shroud cylinder side.
  • the radial outer surface of the intake nozzle becomes a positive pressure surface, and the pressure of the air flowing through the first flow path along the positive pressure surface is higher than the pressure of the mainstream flowing into the fan along the negative pressure surface of the intake nozzle.
  • the merged air has a smaller velocity component in the rotation direction of the fan. Therefore, the intersection angle between the air blown from the second flow path to the front edge side of the blade and the main stream becomes small, so that noise can be reduced.
  • this blower has a relationship of H1> H2
  • the end portion of the shroud cylinder portion on the suction port side is made far from the leading edge of the blade, or the end portion of the intake nozzle on the main plate side is set.
  • the configuration is close to the leading edge of the wing.
  • this blower can further reduce the flow rate of air blown from the second flow path to the front edge side of the blade, and further reduce noise. Further, in this blower, the air flow rate flowing back from the air outlet side of the fan to the flow path formed between the plurality of blades is reduced, so that the blower efficiency of the blower can be improved.
  • FIG. 1 It is sectional drawing which cut the blower which concerns on 1st Embodiment by the virtual plane including the shaft core. It is a top view of FIG. 1 in the II direction. It is a perspective view of the fan provided in the blower which concerns on 1st Embodiment. It is an enlarged view of the IV part of FIG. It is a graph which shows the experimental result which measured the noise level with respect to the flow coefficient about the blower of 1st Embodiment and the blower of a comparative example. It is sectional drawing which shows a part of the blower which concerns on 2nd Embodiment, and is the figure which corresponds to FIG.
  • the blower 1 of the first embodiment is a centrifugal blower used for, for example, an air conditioner or a ventilation device.
  • the blower 1 includes a case 2, a fan 3, a drive unit 4, an intake nozzle 5, and the like.
  • the shaft core CL of the fan 3 may be simply referred to as "shaft core CL”.
  • the axis CL coincides with the rotation axis of the fan 3.
  • the air suction port 6 side of the blower 1 will be referred to as "one side in the shaft core CL direction", and the side opposite to the air suction port 6 of the blower 1 will be described as "the other side in the shaft core CL direction”.
  • the air suction port 6 is simply referred to as a suction port 6.
  • Case 2 has a bell mouth 20 that forms a suction port 6 for sucking air.
  • the bell mouth 20 has a curved surface shape in which the inner diameter gradually decreases from one of the axis CL directions toward the other. Further, the bell mouth 20 is formed in a substantially arc shape in a cross-sectional view (hereinafter referred to as “vertical cross-sectional view”) obtained by cutting in a plane including the axis CL of the fan 3.
  • Case 2 has a front portion 21 formed radially outward from a portion of the bell mouth 20 on one side in the CL direction of the axis.
  • the front surface portion 21 is formed in a plane shape substantially perpendicular to the axis CL of the fan 3.
  • the front surface portion 21 may be formed so as to be inclined with respect to the axis CL of the fan 3.
  • the case 2 has a case cylinder portion 22 extending in a cylindrical shape from a portion of the bell mouth 20 on the other side of the shaft core CL direction to the other side of the shaft core CL direction, and the other side of the case cylinder portion 22 in the shaft core CL direction. It has a case annular portion 23 extending radially outward from the portion of the above.
  • the case cylinder portion 22 is provided with a predetermined gap from the shroud cylinder portion 32 in the area outside the shroud cylinder portion 32 in the radial direction of the fan 3 described later.
  • the axial length H3 of the case cylinder 22 and the axial length of the shroud cylinder 32 correspond to each other.
  • the axial length H3 of the case cylinder portion 22 and the axial length of the shroud cylinder portion 32 are substantially the same.
  • the case cylinder portion 22 and the shroud cylinder portion 32 are formed substantially in parallel.
  • the case annular portion 23 is provided with a predetermined gap from the shroud annular portion 31 in a region on one side of the shroud annular portion 31 of the shroud annular portion 31 described later in the axial CL direction.
  • the case annular portion 23 and the shroud annular portion 31 are also formed substantially in parallel.
  • the fan 3 is a centrifugal fan and is rotatably provided inside the case 2.
  • the fan 3 has a plurality of wings 30, a shroud annular portion 31, a shroud cylinder portion 32, and a main plate 33.
  • the shroud annular portion 31 and the shroud cylinder portion 32 may be collectively referred to as a shroud 34.
  • the fan 3 is a closed fan in which a plurality of wings 30, a shroud 34, and a main plate 33 are integrally formed.
  • the fan 3 is integrally formed by, for example, resin injection molding.
  • the plurality of wings 30 are arranged between the main plate 33 and the shroud 34 at predetermined intervals around the axis CL.
  • one portion 301 in the axis CL direction is connected to the shroud 34, and the other portion 302 in the axis CL direction is connected to the main plate 33.
  • a flow path is formed between the adjacent blades 30 between the shroud 34 and the main plate 33.
  • the flow path will be referred to as an inter-blade flow path.
  • the fan 3 of the first embodiment is a turbofan in which a plurality of blades 30 extend backward in the rotational direction from the leading edge 35 side toward the trailing edge 36 side.
  • the leading edge 35 of the wing 30 has a shape that is convex toward the upstream side of the mainstream sucked from the suction port 6 when viewed from the rotation direction of the wing 30.
  • the leading edge 35 of the wing 30 has an end portion 39 on the suction port 6 side connected to the shroud cylinder portion 32. Then, the leading edge 35 of the wing 30 is inclined inward in the radial direction from the end portion 39 on the suction port 6 side connected to the shroud cylinder portion 32 toward the end portion 40 on the main plate 33 side, and is on the main plate 33 side.
  • the end portion 40 is connected to the main plate 33 radially inside the innermost diameter DIN of the intake nozzle 5, which will be described later.
  • the leading edge 35 of the wing 30 may be referred to as the wing leading edge 35.
  • the shroud 34 is directed from the annular shroud annular portion 31 connected to one portion 301 of the plurality of wings 30 in the CL direction of the axis and the radially inner portion of the shroud annular portion 31 toward the bell mouth 20 side. It has a shroud tubular portion 32 extending in a tubular shape.
  • the shroud 34 is an annular shroud annular portion that extends radially outward from a tubular shroud tubular portion 32 formed on the suction port 6 side and a portion of the shroud tubular portion 32 on the other side in the axis CL direction. It has a part 31 and.
  • the shroud annular portion 31 and the shroud cylinder portion 32 are continuously formed.
  • connection point between the shroud annular portion 31 and the shroud cylinder portion 32 has a smooth curved surface shape in which the vertical cross-sectional view is convex toward the inter-blade flow path side.
  • the main plate 33 is formed in a substantially disk shape.
  • the main plate 33 has a shaft hole 37 in the central portion thereof.
  • the center of the shaft hole 37 coincides with the shaft core CL of the fan 3.
  • a shaft 41 extending from the drive unit 4 is press-fitted and fixed to the shaft hole 37 of the main plate 33.
  • the main plate 33 is inclined outward from the shaft hole 37 in the radial direction and toward the other side in the CL direction of the shaft core.
  • the main plate 33 has a shape that is convex from the outer edge portion toward the axis CL side and toward the suction port 6.
  • the drive unit 4 is an electric motor that outputs torque by energization.
  • the drive unit 4 is fixed to, for example, a housing of an air conditioner.
  • the shaft 41 protruding from the drive unit 4 rotates around the axis of the shaft 41 due to the torque output by the drive unit 4.
  • the intake nozzle 5 is formed in a tubular shape and is provided from the radially inner region of the bell mouth 20 to the radially inner region of the shroud tubular portion 32. .. As shown in FIG. 2, the intake nozzle 5 is fixed to the case 2 by a plurality of support portions 50 projecting radially inward from the bell mouth 20 of the case 2 or the front portion 21, and functions as a stationary wing.
  • the intake nozzle 5 has a shape that gradually reduces in diameter from the bell mouth 20 side toward the shroud cylinder portion 32 side.
  • the intake nozzle 5 has a shape in which the inner diameter and the outer diameter gradually decrease from one side in the axis CL direction toward the other side.
  • one end portion 51 of the intake nozzle 5 in the axis CL direction protrudes from the front portion 21 of the case 2 to one side in the axis CL direction. Therefore, as shown by the arrow F2 in FIG. 4, the air sucked into the fan 3 along the front portion 21 of the case 2 collides with the radially outer surface of the intake nozzle 5, and the air is radially outer of the intake nozzle 5.
  • the surface on the outer side in the radial direction is the positive pressure surface 52
  • the surface on the inner side in the radial direction is the negative pressure surface 53.
  • the intake nozzle 5 has a thick plate thickness at a portion extending from one end 51 in the axis CL direction to the center portion, and a plate thickness at a portion on the other end 54 side in the axis CL direction.
  • the intake nozzle 5 has a blade shape in which the length in the axis CL direction along the inner surface in the radial direction is longer than the length in the CL direction of the axis along the outer surface in the radial direction. Even with this blade shape, the intake nozzle 5 has a positive pressure surface 52 on the outer surface in the radial direction and a negative pressure surface 53 on the inner surface in the radial direction.
  • the first flow path 11 is formed between the intake nozzle 5 and the bell mouth 20. Further, a second flow path 12 is formed between the intake nozzle 5 and the shroud cylinder portion 32. Further, a gap flow path 13 is formed between the inner wall of the case 2 (that is, the case cylinder portion 22 and the case annular portion 23) and the shroud 34 (that is, the shroud cylinder portion 32 and the shroud annular portion 31).
  • the first flow path 11, the second flow path 12, and the gap flow path 13 communicate with each other.
  • the point where the first flow path 11, the second flow path 12, and the gap flow path 13 communicate with each other is referred to as a confluence portion 14.
  • the flow path formed between the case cylinder portion 22 and the shroud cylinder portion 32 is referred to as a cylinder flow path 15, and the case annular portion 23 and the shroud annular portion 31 are referred to.
  • the flow path formed between them may be referred to as an annular flow path 16.
  • the pressure of the air flowing through the first flow path 11 along the positive pressure surface 52 of the intake nozzle 5 is higher than the pressure of the mainstream flowing into the fan 3 along the negative pressure surface 53 of the intake nozzle 5. Therefore, in the configuration of the blower 1 of the first embodiment, the pressure of the merging portion 14 and the air outlet of the fan 3 are compared with the configuration in which the first flow path 11 does not exist as in the configuration of the blower described in Patent Document 1 described above. The differential pressure from the pressure on the 7 side becomes smaller. Therefore, according to the configuration of the blower 1 of the first embodiment, the air flow rate from the air outlet 7 side of the fan 3 through the gap flow path 13 to the confluence portion 14 side is reduced.
  • the merging air has a smaller velocity component in the rotation direction of the fan 3. Therefore, the intersection angle between the air blown from the second flow path 12 to the blade leading edge 35 side and the main stream becomes small, and noise is reduced.
  • the shroud cylinder portion 32 and the intake nozzle 5 are set as follows. That is, as shown in FIG. 4, the distance between the end 38 on the suction port 6 side of the shroud cylinder 32 and the end 54 on the main plate 33 side of the intake nozzle 5 in the axis CL direction is H1. Further, the distance between the end portion 54 on the main plate 33 side of the intake nozzle 5 and the end portion of the blade leading edge 35 closest to the suction port 6 side in the axis CL direction is defined as H2. At this time, the blower 1 of the first embodiment is formed so that the shroud cylinder portion 32 and the intake nozzle 5 have a relationship of H1> H2.
  • H1> H2 is established by extending the shroud cylinder portion 32 to one side in the axis CL direction and moving the end portion 38 of the shroud cylinder portion 32 on the suction port 6 side away from the blade leading edge 35. do.
  • the pressure on the negative pressure surface side of the blade leading edge 35 is the lowest, and the pressure approaches the atmospheric pressure toward one side in the axis CL direction (that is, the suction port 6 side) from there. Will be high. Therefore, as the distance between the end 38 on the suction port 6 side of the shroud cylinder 32 and the wing leading edge 35 increases, the pressure of the merging portion 14 increases with respect to the negative pressure in the vicinity of the wing leading edge 35. Further, by increasing the distance between the end 38 on the suction port 6 side of the shroud cylinder 32 and the wing leading edge 35, the end 38 on the suction port 6 side of the shroud cylinder 32 is the positive of the intake nozzle 5.
  • the pressure of the merging portion 14 becomes higher than the negative pressure in the vicinity of the blade leading edge 35. Therefore, it is possible to reduce the differential pressure between the pressure of the merging portion 14 and the pressure on the air outlet 7 side of the fan 3.
  • H1> H2 is also established by extending the intake nozzle 5 toward the main plate 33 and bringing the end portion 54 of the intake nozzle 5 on the main plate 33 side closer to the blade leading edge 35.
  • the second flow path 12 becomes longer and the pressure loss of the second flow path 12 increases, so that the pressure of the confluence portion 14 becomes the blade. It becomes higher with respect to the negative pressure near the leading edge 35. This also makes it possible to reduce the differential pressure between the pressure of the merging portion 14 and the pressure on the air outlet 7 side of the fan 3.
  • the shroud cylinder portion 32 and the intake nozzle 5 have a relationship of H1> H2, so that the pressure on the air outlet 7 side of the fan 3 and the pressure of the confluence portion 14 are set. It is possible to reduce the differential pressure. As a result, the air flow rate flowing back through the gap flow path 13 from the air outlet 7 side of the fan 3 to the merging portion 14 side is reduced. Therefore, the blower 1 can further reduce the air flow rate blown from the second flow path 12 to the blade leading edge 35 side, and further reduce noise. Further, since the blower 1 reduces the air flow rate flowing back from the air outlet 7 side of the fan 3 to the inter-blade flow path, the blow efficiency of the blower 1 can be improved.
  • blower 100 of the comparative example will be described.
  • the blower 100 of the comparative example is formed so that the shroud cylinder portion 32 and the intake nozzle 5 have a relationship of H1 ⁇ H2.
  • the distance of H2 is the same between the blower 100 of the comparative example and the blower 1 of the first embodiment.
  • the blower 100 of this comparative example was created by the applicant and is not a conventional technique.
  • the blower 100 of the comparative example has a shroud cylinder portion 32 in which the end 38 on the suction port 6 side and the blade leading edge 35 are closer to each other, so that the pressure of the confluence portion 14 is reduced. Is relatively close to the negative pressure near the leading edge 35 of the wing. Further, in the blower 100 of the comparative example, the end 38 on the suction port 6 side of the shroud cylinder portion 32 is farther from the curved portion of the positive pressure surface 52 of the intake nozzle 5 as compared with the blower 1 of the first embodiment. Then, the pressure of the merging portion 14 becomes relatively close to the negative pressure near the leading edge 35 of the wing.
  • the pressure loss of the second flow path 12 is small because the second flow path 12 is shorter than that of the blower 1 of the first embodiment, and the pressure of the merging portion 14 is the leading edge of the blade. It is relatively close to the negative pressure around 35. Therefore, in the blower 100 of the comparative example, the difference pressure between the pressure on the air outlet 7 side of the fan 3 and the pressure on the merging portion 14 is larger than that in the blower 1 of the first embodiment, and the pressure is larger from the air outlet 7 side of the fan 3. The air flow rate flowing back in the gap flow path 13 on the merging portion 14 side is relatively large.
  • FIG. 5 shows the experimental results of measuring the noise level when the flow coefficient is changed in the blower 1 of the first embodiment and the blower 100 of the comparative example described above.
  • the results of measuring the relationship between the flow coefficient and the noise level are plotted for the blower 1 of the first embodiment and the blower 100 of the comparative example, and the results are connected by a solid line.
  • the measurement result of the blower 1 of the first embodiment is shown by the solid line A
  • the measurement result of the blower 100 of the comparative example is shown by the solid line B.
  • the blower 1 of the first embodiment can reduce the noise level in all the flow coefficient ranges as compared with the blower 100 of the comparative example.
  • the blower 1 of the first embodiment can reduce the noise level by 1 dB or more in a predetermined flow coefficient range as compared with the blower 100 of the comparative example.
  • the blower 1 of the first embodiment described above has the following effects.
  • the intake nozzle 5 included in the blower 1 of the first embodiment has a shape that gradually reduces in diameter from the bell mouth 20 side toward the shroud cylinder portion 32 side.
  • the radial outer surface of the intake nozzle 5 becomes the positive pressure surface 52, and the pressure of the air flowing through the first flow path 11 along the positive pressure surface 52 is applied to the fan 3 along the negative pressure surface 53 of the intake nozzle 5.
  • the merging air has a smaller velocity component in the rotation direction of the fan 3. Therefore, since the crossing angle between the air blown from the second flow path 12 to the blade leading edge 35 side and the mainstream becomes small, noise can be reduced.
  • blower 1 of the first embodiment is formed so that the shroud cylinder portion 32 and the intake nozzle 5 have a relationship of H1> H2. That is, by increasing the distance between the end 38 on the suction port 6 side of the shroud cylinder 32 and the wing leading edge 35, the end 38 on the suction port 6 side of the shroud cylinder 32 is the intake nozzle 5. As it approaches the end 51 on the atmosphere side, the pressure at the confluence 14 becomes higher than the negative pressure near the wing leading edge 35.
  • the pressure loss of the second flow path 12 increases with the extension of the second flow path 12, so that the confluence portion The pressure of 14 becomes higher than the negative pressure near the leading edge 35 of the wing. Therefore, since the differential pressure between the pressure on the air outlet 7 side of the fan 3 and the pressure at the merging portion 14 becomes smaller, it is possible to further reduce the air flow rate flowing back through the gap flow path 13. Therefore, the blower 1 can further reduce the air flow rate blown from the second flow path 12 to the blade leading edge 35 side, and further reduce the noise.
  • the blower 1 since the air flow rate flowing back from the air outlet 7 side of the fan 3 to the inter-blade flow path is reduced, the air flows through the inter-blade flow path under the condition that a predetermined air flow rate is blown from the air outlet 7 of the fan 3. It is possible to reduce the air flow rate. Therefore, the blower 1 can improve the blowing efficiency.
  • the case 2 provided in the blower 1 of the first embodiment has a case cylinder portion 22 extending in a cylindrical shape from the bell mouth 20 to the main plate 33 side, and a shroud annular portion from a portion of the case cylinder portion 22 on the main plate 33 side. It has a case annular portion 23 that extends radially outward along 31.
  • the gap flow path 13 includes a tubular flow path 15 formed between the case tubular portion 22 and the shroud tubular portion 32, and an annular flow path 16 formed between the case annular portion 23 and the shroud annular portion 31. have. According to this, it is possible to lengthen the gap flow path 13 by having the gap flow path 13 having the tubular flow path 15 and the annular flow path 16.
  • the pressure loss of the gap flow path 13 increases, and the air flow rate flowing back through the gap flow path 13 can be reduced.
  • the length of the cylinder flow path 15 is increased by extending the axial length H3 of the case cylinder portion 22 and the axial length (H1 + H2) of the shroud cylinder portion 32, the merging portion 14 and the leading edge of the wing can be extended. It is also possible to increase the distance from 35. Therefore, the pressure of the merging portion 14 becomes higher than the negative pressure in the vicinity of the blade leading edge 35, and the air flow rate flowing back through the gap flow path 13 is further reduced. Therefore, the blower 1 can reduce the noise and improve the blowing efficiency by reducing the air flow rate blown from the second flow path 12 to the blade leading edge 35 side.
  • connection portion between the shroud cylinder portion 32 and the shroud annular portion 31 has a curved surface shape in which the vertical cross-sectional view is convex toward the inter-blade flow path side. According to this, the air flowing through the inter-blade flow path is suppressed from being separated from the surface of the shroud 34 on the inter-blade flow path side, and flows along the surface of the shroud 34 on the inter-blade flow path side. Therefore, it is possible to efficiently use the entire region of the inter-blade flow path, and it is possible to improve the blowing efficiency of the blower 1.
  • the wing leading edge 35 has a shape that is convex toward the upstream side of the main stream sucked from the suction port 6 into the inter-blade flow path when viewed from the rotation direction thereof.
  • the end portion 39 of the leading edge 35 of the wing 30 on the suction port 6 side is connected to the shroud cylinder portion 32. According to this, it is possible to integrally form a fan 3 having a plurality of blades 30, a shroud 34, and a main plate 33 by resin injection molding.
  • a surface of the shroud cylinder portion 32 that faces inward in the radial direction, a blade leading edge 35, and the like are formed by a first mold (not shown) that can move in the axis CL direction of the fan 3. It is possible to do. Further, from the second mold (not shown) that can move in the radial and circumferential directions of the fan 3, the surface of the blade 30 facing the rotation direction, the surface of the shroud annular portion 31 facing the main plate 33 side, and the main plate 33. Of these, it is possible to form a surface facing the shroud 34 side.
  • the shroud cylinder portion 32 has a shape in which the inner diameter gradually increases from the other side in the axial direction toward one side in the axial direction.
  • the wing leading edge 35 is inclined inward in the radial direction from the end portion 39 connected to the shroud cylinder portion 32 toward the end portion 40 on the main plate 33 side, and is on the main plate 33 side.
  • the end portion 40 is connected to the main plate 33 radially inside the innermost diameter DIN of the intake nozzle 5. According to this, by arranging the end 40 on the main plate 33 side of the wing leading edge 35 radially inside the innermost diameter DIN of the intake nozzle 5, the negative pressure formed in the vicinity of the wing leading edge 35 causes the negative pressure. It is possible to draw the mainstream inward in the radial direction of the intake nozzle 5.
  • the pressure of the air flowing through the first flow path 11 along the radial outer positive pressure surface 52 of the intake nozzle 5 is higher than the pressure of the mainstream flowing into the fan 3 along the negative pressure surface 53 of the intake nozzle 5. It gets higher. Therefore, the differential pressure between the pressure of the merging portion 14 and the pressure on the air outlet 7 side of the fan 3 can be made smaller, and the air flow rate flowing back through the gap flow path 13 can be further reduced.
  • the intake nozzle 5 included in the blower 1 of the first embodiment has a plate thickness of a portion extending from one end 51 side in the axis CL direction to the center portion on the other end 54 side in the axis CL direction.
  • the shape is thicker than the plate thickness of.
  • the intake nozzle 5 has a shape in which the length in the axis CL direction along the inner surface in the radial direction is longer than the length in the CL direction of the axis along the outer surface in the radial direction. That is, the intake nozzle 5 has a wing shape.
  • the radial outer surface of the intake nozzle 5 becomes the positive pressure surface 52, and the pressure of the air flowing into the first flow path 11 along the positive pressure surface 52 is the fan 3 along the negative pressure surface 53 of the intake nozzle 5. It will be higher than the mainstream pressure flowing into. Therefore, the differential pressure between the pressure of the merging portion 14 and the pressure on the air outlet 7 side of the fan 3 can be made smaller, and the air flow rate flowing back through the gap flow path 13 can be further reduced.
  • the second embodiment will be described.
  • the second embodiment is different from the first embodiment because the shroud 34 and the case 2 are partially modified from the first embodiment and the other parts are the same as those of the first embodiment. Will be explained only.
  • the shroud annular portion 31 has a cylindrical protrusion 60 projecting toward the case annular portion 23 side.
  • the case annular portion 23 has a tubular groove portion 24 at a position corresponding to the tubular protrusion 60.
  • Both the tubular protrusion 60 and the tubular groove portion 24 are formed in a cylindrical shape around the axis CL of the fan 3.
  • the tubular protrusion 60 is fitted inside the tubular groove portion 24 with a predetermined gap.
  • a labyrinth portion 17 is formed in the gap flow path 13 by the cylindrical protrusion 60 and the tubular groove portion 24. That is, the labyrinth portion 17 is also formed around the axis CL of the fan 3.
  • FIG. 6 shows two tubular protrusions 60 and two tubular groove portions 24, the number of the tubular protrusions 60 and the tubular groove portions 24 is not limited to this, and the number of the tubular protrusions 60 and the tubular groove portions 24 can be arbitrarily set. Is possible.
  • the labyrinth portion 17 in the gap flow path 13 by forming the labyrinth portion 17 in the gap flow path 13, it is possible to lengthen the gap flow path 13 and bend the gap flow path 13. Therefore, as the pressure loss in the gap flow path 13 increases, the pressure in the merging portion 14 becomes higher than the negative pressure in the vicinity of the blade leading edge 35. Therefore, according to the configuration of the second embodiment, the air flow rate flowing back through the gap flow path 13 can be further reduced.
  • the second embodiment can exhibit the same action and effect as the first embodiment from the same configuration as the first embodiment.
  • the third embodiment will be described.
  • the third embodiment is a modification of a part of the configuration of the tubular protrusion 60 of the shroud annular portion 31 with respect to the second embodiment, and the other parts are the same as those of the second embodiment. Only the part different from the embodiment will be described.
  • the labyrinth portion 17 is formed in the gap flow path 13 by the tubular protrusion 60 of the shroud annular portion 31 and the tubular groove portion 24 of the case annular portion 23. ..
  • the pressure loss of the gap flow path 13 increases, and the pressure of the merging portion 14 becomes higher than the negative pressure near the blade leading edge 35, so that the air flow rate flowing back through the gap flow path 13 can be reduced. Can be done.
  • the tip portion 61 on the tubular groove portion 24 side of the cylindrical protrusion 60 has a pointed shape.
  • the tubular protrusion 60 has a pointed shape in which the plate thickness gradually decreases from the shroud annular portion 31 side toward the tubular groove portion 24 side, and the tip portion 61 thereof is formed at an acute angle.
  • the flow path area of the gap flow path 13 (specifically, the labyrinth portion 17) is virtually reduced, so that the pressure loss of the gap flow path 13 is further increased. Therefore, the pressure of the merging portion 14 can be made higher than the negative pressure in the vicinity of the blade leading edge 35. Therefore, in the third embodiment, the air flow rate flowing back through the gap flow path 13 can be further reduced as compared with the first and second embodiments.
  • blower 1 of the third embodiment can also exert the same action and effect as the first and second embodiments from the same configuration as that of the first and second embodiments.
  • the fourth embodiment is a modification of a part of the shape of the intake nozzle 5 with respect to the first embodiment, and the other parts are the same as those of the first embodiment. Therefore, only the parts different from the first embodiment are used. explain.
  • the intake nozzle 5 included in the blower 1 of the fourth embodiment has a constant plate thickness in a vertical cross-sectional view.
  • the intake nozzle 5 of the fourth embodiment is also formed in a cylindrical shape in the same manner as that described in the first embodiment described above, and is radially inside the shroud cylinder portion 32 from the radial inner region of the bell mouth 20. It is provided over the area of.
  • the intake nozzle 5 has a shape in which the diameter gradually decreases from one of the axis CL directions toward the other (that is, from the bell mouth 20 side to the shroud cylinder portion 32 side).
  • one end portion 51 of the intake nozzle 5 in the axis CL direction protrudes from the front surface portion 21 of the case 2 to one side in the axis CL direction.
  • the radial outer surface of the intake nozzle 5 becomes the positive pressure surface 52, so that the pressure of the air flowing through the first flow path 11 along the positive pressure surface 52 Is higher than the mainstream pressure flowing into the fan 3 along the negative pressure surface 53 of the intake nozzle 5.
  • the shroud cylinder portion 32 and the intake nozzle 5 are formed so as to have a relationship of H1> H2. Therefore, the differential pressure between the pressure of the merging portion 14 and the pressure on the air outlet 7 side of the fan 3 becomes small, and the air flow rate flowing back through the gap flow path 13 is reduced. Therefore, the blower 1 of the fourth embodiment can also exert the same action and effect as the first embodiment from the same configuration as that of the first embodiment.
  • blower 1 has been described as being used for, for example, an air conditioner or a ventilation device, but the present invention is not limited to this, and the blower 1 can be used for various purposes.
  • the fan 3 provided in the blower 1 has been described as, for example, a turbo fan, but the fan 3 is not limited to this, and the fan 3 can be various centrifugal fans such as a radial fan and a sirocco fan.
  • the present disclosure is not limited to the above-described embodiment, and can be changed as appropriate. Further, the above embodiments are not unrelated to each other, and can be appropriately combined unless the combination is clearly impossible. Further, in each of the above embodiments, it goes without saying that the elements constituting the embodiment are not necessarily essential except when it is clearly stated that they are essential or when they are clearly considered to be essential in principle. stomach. Further, in each of the above embodiments, when numerical values such as the number, numerical values, quantities, and ranges of the constituent elements of the embodiment are mentioned, when it is clearly stated that they are particularly essential, and when it is clearly limited to a specific number in principle. It is not limited to the specific number except when it is done. Further, in each of the above embodiments, when the shape, positional relationship, etc. of the constituent elements are referred to, the shape, the shape, etc. It is not limited to the positional relationship.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
PCT/JP2021/033321 2020-10-21 2021-09-10 送風機 Ceased WO2022085332A1 (ja)

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Application Number Priority Date Filing Date Title
JP2020-176573 2020-10-21
JP2020176573A JP7413973B2 (ja) 2020-10-21 2020-10-21 送風機

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Publication number Priority date Publication date Assignee Title
WO2025197433A1 (ja) * 2024-03-18 2025-09-25 株式会社デンソー 遠心送風機

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3011693A (en) * 1956-12-05 1961-12-05 Clarage Fan Company Apparatus relating to centrifugal wheel inlet boundary control
CN210440276U (zh) * 2019-07-22 2020-05-01 珠海格力电器股份有限公司 用于离心风机的叶轮组件、离心风机、空调器及空气净化器
US20200200187A1 (en) * 2017-07-18 2020-06-25 Ka Group Ag Housing For A Fluid Machine, In Particular For A Radial Fan

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3011693A (en) * 1956-12-05 1961-12-05 Clarage Fan Company Apparatus relating to centrifugal wheel inlet boundary control
US20200200187A1 (en) * 2017-07-18 2020-06-25 Ka Group Ag Housing For A Fluid Machine, In Particular For A Radial Fan
CN210440276U (zh) * 2019-07-22 2020-05-01 珠海格力电器股份有限公司 用于离心风机的叶轮组件、离心风机、空调器及空气净化器

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