WO2022190818A1 - Soufflante - Google Patents

Soufflante Download PDF

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Publication number
WO2022190818A1
WO2022190818A1 PCT/JP2022/006629 JP2022006629W WO2022190818A1 WO 2022190818 A1 WO2022190818 A1 WO 2022190818A1 JP 2022006629 W JP2022006629 W JP 2022006629W WO 2022190818 A1 WO2022190818 A1 WO 2022190818A1
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WO
WIPO (PCT)
Prior art keywords
nozzle
flow path
air
main plate
bell mouth
Prior art date
Application number
PCT/JP2022/006629
Other languages
English (en)
Japanese (ja)
Inventor
隆裕 中嶋
Original Assignee
株式会社デンソー
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
Priority claimed from JP2021190408A external-priority patent/JP2022140271A/ja
Application filed by 株式会社デンソー filed Critical 株式会社デンソー
Publication of WO2022190818A1 publication Critical patent/WO2022190818A1/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
    • F04D29/40—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

Definitions

  • the present disclosure relates to blowers.
  • the blower described in Patent Document 1 has a centrifugal fan arranged inside a case provided with a bell mouth that forms an air suction port.
  • the air sucked from the inside of the bell mouth flows from the leading edge side of the blades through the flow path between the blades and is blown out from the air outlet on the trailing edge side of the blades.
  • the inner peripheral surface of the shroud of the fan and the inner peripheral surface of the bell mouth are formed to have substantially no level difference, so that air is smoothly sucked into the fan from the bell mouth.
  • An object of the present disclosure is to provide a blower capable of improving blowing efficiency and reducing noise by reducing the amount of air that flows backward from the air outlet side of the fan to the suction port side.
  • a blower includes a case, a fan, a nozzle, and a channel partition member.
  • the case has a bell mouth that forms an air intake for sucking air.
  • the fan includes a main plate that is rotatable about the axis inside the case, a plurality of blades arranged around the axis and connected to the main plate, and a portion of the plurality of blades that is connected to the opposite side of the main plate.
  • the nozzle is formed in a cylindrical shape and provided in a region radially inside the bell mouth.
  • the channel partitioning member is intermittently provided in the circumferential direction between the bell mouth and the nozzle, and partitions the space between the nozzle and the bell mouth into a plurality of partition channels through which air flows.
  • backflow air the amount of air that flows back to the suction port side from the shroud and the gap between the case
  • the blower does not have a flow path partitioning member, the backflow air may straddle the end of the nozzle on the side opposite to the main plate and flow inside the nozzle, increasing the speed and volume of the air.
  • the space between the nozzle and the bell mouth is partitioned into a plurality of partition channels by a channel partitioning member intermittently provided between the bell mouth and the nozzle in the circumferential direction. By doing so, it is possible to increase the pressure loss of the counterflow air passing through the plurality of partition passages. Therefore, according to one aspect of the present disclosure, it is possible to reduce the wind speed and the wind volume of the counterflow air that flows inside the nozzle across the end of the nozzle on the side opposite to the main plate, thereby improving the blowing efficiency of the blower.
  • the flow path partition member increases the pressure loss of the backflow air passing through the plurality of partition flow paths, thereby reducing the wind speed distribution of the backflow air in the circumferential direction. is possible. Therefore, according to one aspect of the present disclosure, fan noise can be reduced.
  • a blower includes a case, a fan, a nozzle, and a plurality of flow path partition members.
  • the case has a bell mouth that forms an air intake for sucking air.
  • the fan includes a main plate that is rotatable about the axis inside the case, a plurality of blades arranged around the axis and connected to the main plate, and a portion of the plurality of blades that is connected to the opposite side of the main plate.
  • the nozzle is formed in a cylindrical shape and provided in a region radially inside the bell mouth.
  • a plurality of flow path partitioning members are provided between the bell mouth and the nozzle, and partition the space between the nozzle and the bell mouth into a plurality of partition flow paths through which air flows.
  • the air velocity of the air that flows backward from the air outlet side of the fan to the suction port side inside the nozzle through the plurality of partition passages in the space formed between the bellmouth and the nozzle is made uniform.
  • the plurality of flow path partitioning members can reduce the circumferential wind speed distribution of the backflow air across the nozzles, thereby reducing the noise of the blower.
  • the backflow It is possible to reduce the volume of air and improve the blowing efficiency of the blower.
  • FIG. 2 is a cross-sectional view of the fan according to the first embodiment cut along a virtual plane including the axis;
  • FIG. 2 is a cross-sectional view taken along line II-II of FIG. 1; It is an enlarged view of the III part of FIG. 1, and is a figure which showed the flow of the air in face mode. It is an enlarged view of the III part of FIG. 1, and is the figure which showed the flow of the air in foot mode or defroster mode.
  • FIG. 3 is a diagram of a portion corresponding to FIG. 2 in the blower according to the second embodiment;
  • FIG. 3 is a diagram of a portion corresponding to FIG. 2 in the blower according to the third embodiment;
  • FIG. 10 is a diagram of a portion corresponding to FIG.
  • FIG. 10 is a diagram of a portion corresponding to FIG. 2 in the blower according to the fourth embodiment;
  • FIG. 10 is a diagram of a portion corresponding to FIG. 2 in the blower according to the fifth embodiment;
  • FIG. 3 is a diagram of a portion corresponding to FIG. 2 in the blower of the comparative example, and is a diagram showing the flow of air in the foot mode or the defroster mode;
  • FIG. 4 is a diagram of a portion corresponding to FIG. 3 in the blower of the comparative example, and is a diagram showing the flow of air in the face mode;
  • FIG. 4 is a diagram of a portion corresponding to FIG.
  • FIG. 3 in the blower of the comparative example, and is a diagram showing the flow of air in the foot mode or the defroster mode; It is sectional drawing which cut
  • 13 is a cross-sectional view taken along line XIII-XIII of FIG. 12;
  • FIG. 13 is an enlarged view of the XIV portion of FIG. 12, showing the airflow in the face mode;
  • FIG. 13 is an enlarged view of the XIV portion of FIG. 12, showing air flow in foot mode or defroster mode;
  • the blower 1 according to the first embodiment is a centrifugal blower used, for example, in a vehicle air conditioner.
  • the blower 1 includes a case 10, a fan 20, a drive section 50, a nozzle 60, a flow path partition member 70, and the like. It should be noted that the fan 20 and the drive unit 50 are omitted in FIG. 2 for the sake of clarity. This also applies to FIGS. 5 to 9 and 13, which will be referred to in embodiments and comparative examples to be described later.
  • the axis CL of the fan 20 may be simply referred to as "the axis CL".
  • the axis CL coincides with the rotation center of the fan 20 .
  • the side of the air inlet 2 of the blower 1 will be referred to as “one side in the axial direction”, and the side opposite to the air inlet 2 of the blower 1 will be referred to as “the other side in the axial direction”.
  • the air suction port 2 will simply be referred to as the suction port 2 .
  • the case 10 is a member that forms at least part of the air passage of the vehicle air conditioner.
  • the air passage of a vehicle air conditioner is generally provided with an air cooling device such as an evaporator, an air heating device such as a heater core or an electric heater, and a plurality of flow path switching doors. there is Therefore, in the vehicle air conditioner, the pressure loss of the air flowing through the air passage may change depending on the air conditioning mode.
  • the case 10 has, on the upstream side of the fan 20, a bell mouth 11 that forms an air inlet 2 for sucking air.
  • the bell mouth 11 has a curved shape in which the inner diameter gradually decreases from one side to the other side in the axial direction.
  • the bell mouth 11 has a substantially arcuate radially inner surface in a cross-sectional view obtained by cutting along a plane including the axial center CL of the fan 20 (hereinafter referred to as a “longitudinal cross-sectional view”). .
  • the case 10 has a front wall 12 formed radially outward from a portion on one side of the bell mouth 11 in the axial direction.
  • the front wall 12 is formed in a planar shape substantially perpendicular to the axial center CL of the fan 20 . Note that the front wall 12 may be formed so as to be inclined with respect to the axial center CL of the fan 20 .
  • the case 10 has an upstream case 13 extending from a radially outer portion of the front wall 12 to one side in the axial direction.
  • the case 10 includes a case tubular portion 14 that extends in a tubular shape from a portion on the other axial side of the bell mouth 11 toward the other axial direction, and a portion of the case tubular portion 14 that extends from the portion on the other axial side in the axial direction. and a case annular portion 15 extending radially outward.
  • the case 10 also has a downstream side case 16 extending from a radially outer portion of the case annular portion 15 toward the other side in the axial direction.
  • Each part of the case 10 may be composed of a plurality of members, or may be integrally molded.
  • the case tubular portion 14 is provided with a predetermined gap from the shroud tubular portion 32 in a radially outer region of the shroud tubular portion 32 of the fan 20 to be described later. Further, the case annular portion 15 is provided with a predetermined gap from the shroud annular portion 31 in a region on one side in the axial direction of the shroud annular portion 31 of the fan 20 , which will be described later.
  • the case tubular portion 14 and the shroud tubular portion 32 are provided substantially parallel, and the case annular portion 15 and the shroud annular portion 31 are also provided substantially parallel.
  • the fan 20 is a centrifugal fan (specifically, a turbo fan) and is rotatably provided inside the case 10 .
  • the fan 20 has a main plate 21 , a plurality of blades 22 , a shroud annular portion 31 and a shroud tubular portion 32 .
  • the shroud annular portion 31 and the shroud cylinder portion 32 may be collectively referred to as the shroud 30 .
  • the fan 20 is a closed fan in which a main plate 21, a plurality of blades 22, and a shroud 30 are integrally formed.
  • the fan 20 is integrally formed by resin injection molding, for example.
  • the main plate 21 is formed in a substantially disk shape and arranged inside the case 10 .
  • the main plate 21 is inclined radially outward from the central portion toward the other side in the axial direction.
  • the main plate 21 has a shape that protrudes toward the suction port 2 side from the outer edge toward the central portion.
  • a shaft 51 extending from the driving portion 50 is fixed to the central portion of the main plate 21 .
  • the main plate 21 is provided inside the case 10 so as to be rotatable around the axis.
  • a plurality of blades 22 are arranged at predetermined intervals around the axis between the main plate 21 and the shroud 30 .
  • the plurality of blades 22 are connected to the shroud 30 at one axial portion 23 (that is, the portion 23 opposite the main plate), and are connected to the main plate 21 at the other axial portion 24 .
  • a flow path is formed between the adjacent blades 22 between the shroud 30 and the main plate 21 .
  • the channel is called inter-blade channel 25 .
  • the fan 20 rotates, the air sucked from the suction port 2 passes through the inter-blade flow path 25 from the leading edge 26 side of the blade 22 and is blown out from the air outlet 28 formed at the trailing edge 27 side of the blade 22.
  • the plurality of blades 22 extend rearward in the rotational direction of the fan 20 from the front edge 26 toward the rear edge 27 . That is, the fan 20 of the first embodiment is a turbo fan.
  • the leading edge 26 of the blade 22 is connected to the shroud tubular portion 32 at one end 29 in the axial direction.
  • the leading edge 26 of the blade 22 is inclined radially inward from an end 29 on one side in the axial direction toward an end 291 on the other side in the axial direction. 291 is connected to the main plate 21 radially inside the innermost diameter of the nozzle 60 .
  • the leading edge 26 of the blade 22 may be referred to as the leading edge 26 in the following description.
  • the shroud 30 includes a tubular shroud tubular portion 32 formed on the suction port 2 side, and an annular shroud extending radially outward from a portion of the shroud tubular portion 32 on the other side in the axial direction. and an annular portion 31 .
  • the shroud annular portion 31 is an annular portion connected to one portion 23 of the plurality of blades 22 in the axial direction (that is, the portion 23 of the plurality of blades 22 on the side opposite to the main plate).
  • the shroud tubular portion 32 is a portion of the shroud annular portion 31 that extends in a tubular shape from a radially inner portion toward the side opposite to the main plate.
  • the shroud annular portion 31 and the shroud tubular portion 32 are formed continuously.
  • the shroud annular portion 31 has a smooth curved shape that is convex toward the inter-blade flow path 25 when viewed in longitudinal section. As a result, the air flowing through the inter-blade passage 25 is prevented from separating from the surface of the shroud 30 on the inter-blade passage 25 side, and flows along the surface of the shroud 30 on the inter-blade passage 25 side.
  • the drive unit 50 is an electric motor that outputs torque when energized.
  • a shaft 51 protruding from the driving portion 50 is fixed to the main plate 21 of the fan 20 .
  • the torque output from the drive unit 50 causes the shaft 51 and the fan 20 to rotate about their axes.
  • the nozzle 60 is formed in a tubular shape, and is provided from a radially inner region of the bell mouth 11 to a radially inner region of the shroud tubular portion 32 .
  • the nozzle 60 is fixed to the case 10 by a flow path partitioning member 70, which will be described later, and functions as a stationary blade.
  • An end portion 61 of the nozzle 60 on the side opposite to the main plate (that is, one end portion of the nozzle 60 in the axial direction) is closer to the opposite side of the main plate than the front wall 12 of the case 10 (that is, one side in the axial direction). protrudes to
  • the nozzle 60 has a shape that expands radially outward from the central portion toward the end portion 61 on the side opposite to the main plate.
  • the nozzle 60 has a shape in which the outer diameter gradually decreases from the end 61 on the side opposite to the main plate toward the end 62 on the side of the main plate 21 (that is, from one side to the other in the axial direction).
  • the nozzle 60 has a thickness of a portion extending from the end 61 on the opposite side of the main plate (that is, one end in the axial direction) to the center.
  • the plate thickness gradually decreases toward the portion 62 (that is, the other end portion in the axial direction).
  • the nozzle 60 has a so-called blade shape in which the length in the axial direction along the radially inner surface is longer than the length in the axial direction along the radially outer surface.
  • a channel partitioning member 70 is provided between the bell mouth 11 and the nozzle 60. As shown in FIG.
  • the channel partitioning member 70 is connected to the bell mouth 11 at its radially outer portion, and is connected to the nozzle 60 at its radially inner portion.
  • the flow path partitioning member 70 is provided intermittently in the circumferential direction between the bell mouth 11 and the nozzle 60, and divides the space between the nozzle 60 and the bell mouth 11 into a plurality of partition flow paths 73 through which air flows.
  • the number of flow path partition members 70 is more than twice the number (for example, 2 to 4) required to support the nozzles 60 so that the pressure loss of the air passing through the plurality of partition flow paths 73 increases. It is preferable to configure with a number (for example, 8 or more).
  • the air flow in the axial direction and the circumferential direction compared to the air flow in each partition flow path 73 when the flow path partition member 70 is the number required to support the nozzle 60 (for example, 2 to 4) can be reduced (e.g., 8 or more).
  • the blower 1 of the first embodiment illustrated in FIG. 2 has 20 passage partition members 70 .
  • By increasing the number of flow path partitioning members 70 in this way it is possible to increase the pressure loss of the air passing through each partitioning flow path 73 .
  • Further, by increasing the number of the flow path partitioning members 70 it is possible to reduce the air flow in the axial direction and the circumferential direction in each partition flow path 73 and to rectify the air flow in each partition flow path 73.
  • the number of flow path partitioning members 70 is not limited to the number shown in FIG.
  • each channel partitioning member 70 preferably has a large thickness when viewed from the axial direction in order to increase the pressure loss of the air passing through the plurality of partitioning channels 73 .
  • the thickness of each channel partition member 70 is preferably about 1.5 to 3.0 mm, more preferably 2.0 to 2.5 mm. is more preferred.
  • each partitioning flow path 73 can cross-sectional area of the flow path viewed from the direction.
  • the distance of each partitioning flow path 73 in the axial direction is increased.
  • the flow path partitioning member 70 is radially provided between the nozzle 60 and the bell mouth 11 . Further, the channel partitioning member 70 is provided over the entire circumference between the bell mouth 11 and the nozzle 60 . In addition, the channel partitioning members 70 are provided at uniform intervals in the circumferential direction between the bell mouth 11 and the nozzles 60 . Note that the uniform intervals in the circumferential direction are uniform within a range including manufacturing tolerances. For example, if it is within 5%, it shall be included in the uniform range.
  • An end portion 71 of the flow path partitioning member 70 on the side opposite to the main plate is located closer to the main plate 21 than an end portion 61 of the nozzle 60 on the side opposite to the main plate.
  • the end portion 72 of the flow path partitioning member 70 on the main plate 21 side is located on the opposite side of the main plate than the end portion 62 of the nozzle 60 on the main plate 21 side. Therefore, the flow path partitioning member 70 does not block the flow of the main flow that is sucked into the fan 20 from the flow path on the upstream side of the nozzle 60 through the suction port 2 radially inward of the nozzle 60 .
  • the space on one side in the axial direction with respect to the partition flow path 73 is defined as the first space. It is called 1 channel 81 .
  • a space on the other side in the axial direction from the partitioning channel 73 between the nozzle 60 and the case cylindrical portion 14 is called a second channel 82 .
  • a space between the nozzle 60 and the shroud tube portion 32 is called a third flow path 83 .
  • the space between the shroud 30 (specifically, the shroud tubular portion 32 and the shroud annular portion 31) and the inner wall of the case 10 (specifically, the case tubular portion 14 and the case annular portion 15) is filled with a gap flow. Call it Road 84.
  • the air sucked by the fan 20 along the front wall 12 of the case 10 collides with the radially outer surface of the nozzle 60, and flows along the surface into the first flow path.
  • the air flowing backward from the air outlet 28 side to the suction port 2 side flows through the gap flow path 84 .
  • the air that flows back through the gap flow path 84 contains a velocity component in the rotation direction of the fan 20 .
  • the air flowing through the gap flow paths 84 indicated by arrows F4 and F5 and the air flowing in from the first flow path 81 indicated by arrow F2 merge in the second flow path 82, and then move toward the second flow path as indicated by arrow F3. It flows through the third channel 83 and is sucked into the inter-blade channel 25 together with the main stream from the blade leading edge 26 side.
  • the pressure of the air flowing along the radially outer surface of the nozzle 60 is higher than the pressure of the main stream flowing into the fan 20 along the radially inner surface of the nozzle 60 . Therefore, the pressure difference between the pressure in the first flow path 81, the partition flow path 73 and the second flow path 82 and the pressure on the side of the air outlet 28 of the fan 20 becomes small, and the air outlet 28 side of the fan 20 increases the gap flow path. The amount of air flowing back through 84 can be reduced.
  • the main stream is sucked into the inter-blade passage 25 from the front edge 26 side of the fan 20 along the radially inner surface of the nozzle 60, as indicated by arrow F1 in FIG.
  • the air conditioner is set to the foot mode or the defroster mode
  • the pressure loss in the flow path on the downstream side of the blower 1 is greater than that in the face mode. Therefore, as the rotation speed of the fan 20 increases, the difference between the pressure on the side of the air outlet 28 of the fan 20 and the pressure on the side of the suction port 2 becomes larger than the pressure difference in the face mode.
  • the backflow air flows from the second flow path 82 through the partition flow path 73 and the first flow path 81 as indicated by the dashed arrow F6 in FIG. It tries to flow inside the nozzle 60 across the end 61 of the nozzle 60 on the side opposite to the main plate.
  • the pressure of the backflow air passing through the partitioned channels 73 is The losses are increased, and the wind speed and volume of the backflow air are reduced.
  • the inventor's research has revealed that the backflow air that tries to flow inside the nozzle 60 across the end 61 of the nozzle 60 on the side opposite to the main plate has a large wind speed distribution in the circumferential direction.
  • the space between the nozzle 60 and the bell mouth 11 is partitioned into a plurality of partitioned channels 73 by the channel partitioning member 70, the pressure of the backflow air passing through the partitioned channels 73 is Loss is increased, and the circumferential wind velocity distribution of the backflow air is reduced.
  • ribs 700 are provided between the bellmouth 11 and the nozzle 60 in the number (for example, four) required to support the nozzle 60 .
  • the rib 700 has a negligibly small function and effect as flow resistance of backflow air.
  • FIG. 10 shows the flow of air when the air conditioner is set to the face mode in the blower 100 of the comparative example.
  • the air flow when the air conditioner is set to the face mode and the fan 1 is operated is the same as the fan 1 of the first embodiment. be. Therefore, even in the blower 100 of the comparative example, when the air conditioner is in the face mode, it is possible to reduce the amount of backflow air, improve the blowing efficiency, and reduce noise.
  • FIG. 11 shows the flow of air when the air conditioner is set to the foot mode or the defroster mode in the blower 100 of the comparative example.
  • the fan 20 rotates, the main stream is sucked into the inter-blade passage 25 from the front edge 26 side of the fan 20 along the radially inner surface of the nozzle 60, as indicated by arrow F1 in FIG.
  • the pressure loss in the flow path on the downstream side of the blower 100 is greater than in the face mode.
  • the plurality of arrows F8 to F13 shown in FIG. 9 indicate locations where the wind speed of the backflow air straddling the nozzle 60 is high.
  • the wind speed of the backflow air across the nozzle 60 is low.
  • the blower 100 of the comparative example when the air conditioner is in the foot mode or the defroster mode, the backflow air across the nozzle 60 has a large circumferential wind speed distribution and is joined with the main stream, and the front edge 26 side of the blade 22 There is a risk that the noise will increase by flowing into the
  • the blower 1 of the first embodiment includes flow path partitioning members 70 intermittently provided between the bell mouth 11 and the nozzle 60 in the circumferential direction.
  • the channel partitioning member 70 partitions the space between the nozzle 60 and the bellmouth 11 into a plurality of partitioning channels 73 through which air flows. According to this, by partitioning the space between the nozzle 60 and the bell mouth 11 into a plurality of partitioned channels 73 by the channel partitioning member 70, the pressure loss of the backflow air passing through the plurality of partitioned channels 73 is increased. It is possible. Therefore, the blower 1 can reduce the wind speed and air volume of the backflow air and improve the blowing efficiency.
  • the backflow air across the nozzle 60 has a large circumferential wind speed distribution, and the backflow air having the wind speed distribution intersects with the main stream and flows toward the front edge 26 of the blade 22. It was found that the noise increased as the water flowed in.
  • the pressure loss of the backflow air passing through the partition flow path 73 is increased by the flow path partition member 70, so that the wind velocity distribution of the backflow air across the nozzle 60 in the circumferential direction is increased. can be reduced. Therefore, the blower 1 can reduce the noise generated when the backflow air flows into the leading edge 26 side of the blade.
  • the channel partitioning member 70 is radially provided between the nozzle 60 and the bellmouth 11 so as to increase the pressure loss of the air flowing through the plurality of partitioning channels 73. . According to this, a specific arrangement of the plurality of channel partitioning members 70 is exemplified.
  • the end portion 71 of the flow path partitioning member 70 on the side opposite to the main plate is located closer to the main plate 21 than the end portion 61 of the nozzle 60 on the side opposite to the main plate. Further, the end portion 72 of the flow path partitioning member 70 on the main plate 21 side is located on the opposite side of the main plate than the end portion 62 of the nozzle 60 on the main plate 21 side. According to this, the flow path partitioning member 70 does not block the flow of the main flow that is sucked into the fan 20 from the flow path on the upstream side of the nozzle 60 through the radially inner side of the nozzle 60 .
  • the channel partitioning members 70 are provided at regular intervals in the circumferential direction between the bellmouth 11 and the nozzles 60 . According to this, by uniformly increasing the pressure loss of the counterflow air passing through the partition passage 73 in the circumferential direction, the wind speed and the air volume of the counterflow air flowing through the partition passage 73 are reduced. It is possible to reduce the distribution. Moreover, even if the position of the wind speed distribution in the circumferential direction of the backflow air across the nozzle 60 changes due to the usage conditions of the blower 1, it is possible to reduce the wind speed distribution.
  • the channel partitioning member 70 is provided along the entire circumference between the bell mouth 11 and the nozzle 60 . According to this, by increasing the pressure loss of the backflow air passing through the partition passage 73 over the entire circumference, the wind speed and air volume of the backflow air flowing through the partition passage 73 are reduced, and as a result, the wind speed distribution is reduced. can be reduced. Moreover, even if the position of the wind speed distribution in the circumferential direction of the backflow air across the nozzle 60 changes due to the usage conditions of the blower 1, it is possible to reduce the wind speed distribution.
  • the fan 20 is a turbo fan whose blades 22 extend rearward in the rotational direction from the leading edge 26 toward the trailing edge 27. and the air outlet 28, the flow rate of the backflow air tends to increase. Even in the blower 1 having the turbofan having such characteristics, it is possible to exhibit the effects of improving the blowing efficiency and reducing the noise.
  • the number of channel partition members 70 is more than twice the number required to support the nozzles 60 . According to this, by increasing the number of the flow path partitioning members 70, the flow path cross-sectional area of each partition flow path 73 becomes smaller, so that the pressure loss of the backflow air passing through the partition flow path 73 can be increased. It is possible. Therefore, it is possible to reduce the air volume of the backflow air and reduce the wind velocity distribution of the backflow air in the circumferential direction.
  • the channel partitioning member 70 provided between the bell mouth 11 and the nozzle 60 is configured in a net shape. Meshes of the mesh-shaped flow path forming member serve as a plurality of partition flow paths 73 .
  • the mesh-like channel partition member 70 is provided along the entire circumference between the bell mouth 11 and the nozzle 60 so as to increase the pressure loss of the air passing through the plurality of partition channels 73 .
  • the thickness of the net-like flow path forming member, the flow path cross-sectional area of the plurality of partition flow paths 73, and the flow path length of the plurality of partition flow paths 73 in the axial direction can be set arbitrarily.
  • the shape of the plurality of partitioning channels 73 is rectangular, but the shape of the plurality of partitioning channels 73 is not limited to this, and may be, for example, circular, elliptical, polygonal, or a combination thereof. , can be set arbitrarily.
  • the net-like flow path partition member 70 provided in the blower 1 of the second embodiment described above also increases the pressure loss of the backflow air passing through the plurality of partition flow paths 73, so that the wind speed and air volume of the backflow air are reduced, It is possible to reduce the circumferential wind velocity distribution of the backflow air straddling the nozzle 60 . Therefore, in the blower 1 of the second embodiment as well, the blowing efficiency can be improved and the noise can be reduced.
  • the flow path partitioning member 70 is provided only within a predetermined angular range set at a plurality of locations in the circumferential direction between the bell mouth 11 and the nozzle 60 .
  • arrows R1 to R3 indicate the predetermined angular range in which the flow path partition member 70 is provided.
  • three predetermined angle ranges are set.
  • the predetermined angular range in which the flow path partitioning member 70 is provided is set to a position where the wind speed of the backflow air across the nozzle 60 would be high if the flow path partitioning member 70 were not provided.
  • the location can be set by experiment, simulation, or the like.
  • the blower 1 of the third embodiment has a narrow space between the plurality of flow path partitioning members 70 and a plurality of flow path partitioning members 70 so that the wind velocity of the backflow air across the nozzles 60 is made uniform.
  • 70 has a part with a wide space
  • blower 1 of the third embodiment described above by arranging the locations where the intervals between the plurality of flow path partitioning members 70 are narrow at locations where the backflow air has a high wind speed, It is possible to equalize the wind speed of the backflow air over the direction. Therefore, it is possible to reduce the circumferential wind velocity distribution of the backflow air straddling the nozzle 60 and reduce the wind velocity and air volume of the backflow air. Further, in the third embodiment, it is possible to adopt a configuration in which the channel partitioning member 70 is not provided more than necessary.
  • the channel partitioning members 70 are provided between the bell mouth 11 and the nozzle 60 at uneven intervals in the circumferential direction.
  • the non-uniform intervals in the circumferential direction refer to non-uniform intervals that do not include manufacturing tolerances if they are evenly arranged in the circumferential direction. If the difference in cross-sectional area between the plurality of partition channels 73 is greater than 5%, it can be said to be non-uniform.
  • the blower 1 of the fourth embodiment can increase the pressure loss of the backflow air passing through the plurality of partition passages 73 and equalize the wind speed of the backflow air. That is, it is possible to reduce the circumferential wind velocity distribution of the backflow air straddling the nozzle 60 and reduce the wind velocity and air volume of the backflow air.
  • the fifth embodiment is a modification of the third embodiment.
  • the flow path partitioning members 70 are provided only in predetermined angular ranges set at six points in the circumferential direction between the bell mouth 11 and the nozzle 60 .
  • arrows R1 to R6 indicate the predetermined angular range in which the channel partition member 70 is provided.
  • the predetermined angular range in which the flow path partitioning member 70 is provided is set at a position where the wind speed of the backflow air across the nozzle 60 would be high if the flow path partitioning member 70 were not provided.
  • the location can be set by experiment, simulation, or the like. That is, the predetermined angle range in which the flow path partition member 70 is provided is not limited to the six positions shown in FIG. 8, and can be set arbitrarily.
  • the blower 1 of the fifth embodiment in order to equalize the wind velocity of the backflow air across the nozzles 60, the portions where the intervals between the plurality of flow path partitioning members 70 are narrow and the plurality of flow path partitioning members 70 has a part with a wide space
  • the blower 1 of the fifth embodiment can also achieve the same effects as those of the third embodiment and the like.
  • the sixth embodiment has a configuration in which the shroud tubular portion 32 is omitted from the first embodiment, and the rest is the same as the first embodiment. Therefore, the parts different from the first embodiment will be described.
  • the blower 1 of the sixth embodiment also includes a case 10, a fan 20, a drive section 50, a nozzle 60, a flow path partition member 70, and the like.
  • the fan 20 has a main plate 21 , multiple blades 22 and a shroud 30 .
  • the shroud 30 has a shroud annular portion 31 connected to the portion 23 of the plurality of blades 22 on the side opposite to the main plate.
  • the shroud 30 has a portion (that is, the shroud cylinder portion 32 described in the first embodiment) that extends cylindrically from the radially inner portion of the shroud annular portion 31 toward the side opposite to the main plate. not.
  • the nozzle 60 is formed in a tubular shape, and is provided from a radially inner region of the bell mouth 11 to a radially inner region of the case tubular portion 14 .
  • Other configurations of the fan 1 of the sixth embodiment are substantially the same as those described in the first embodiment.
  • a plurality of channel partitioning members 70 are provided between the bell mouth 11 and the nozzle 60.
  • a plurality of flow path partitioning members 70 are intermittently provided in the circumferential direction between the bell mouth 11 and the nozzle 60 to form a plurality of partition flow paths 73 through which air flows in the space between the nozzle 60 and the bell mouth 11. partitioning.
  • the number, thickness, etc. of the plurality of channel partitioning members 70 are the same as those described in the first embodiment. That is, the plurality of flow path partitioning members 70 increase the pressure loss of the air passing through each partition flow path 73, reduce the air flow in the axial direction and the circumferential direction in each partition flow path 73, and The number, thickness, etc. of the passages 73 are set for the purpose of rectifying the air flow of the passages 73 .
  • a plurality of flow path partitioning members 70 are radially provided between the nozzle 60 and the bell mouth 11 .
  • a plurality of flow path partitioning members 70 are provided over the entire circumference between the bell mouth 11 and the nozzle 60 .
  • the plurality of flow path partitioning members 70 are provided at regular intervals in the circumferential direction between the bell mouth 11 and the nozzle 60 .
  • the number, shape, arrangement, etc. of the channel partitioning members 70 are not limited to those shown in FIG. 13, and the configurations described in the second to fifth embodiments can be applied.
  • a space on one side in the axial direction with respect to the partition flow path 73 is provided. It is called the first channel 81 .
  • a space on the other side in the axial direction from the partitioning channel 73 between the nozzle 60 and the case cylindrical portion 14 is called a second channel 82 .
  • the space between the shroud 30 and the inner wall of the case 10 is called a gap channel 84 .
  • the air sucked by the fan 20 along the front wall 12 of the case 10 collides with the radially outer surface of the nozzle 60, and flows along the surface into the first flow path. 81 ⁇ partition channel 73 ⁇ second channel 82 . Then, the air is sucked into the inter-blade passage 25 from the blade leading edge 26 side.
  • the pressure at the air outlet 28 of the fan 20 becomes higher than the pressure at the suction port 2 side of the fan 20 . Therefore, as indicated by arrows F4 and F5, the air flowing backward from the air outlet 28 side to the suction port 2 side flows through the gap flow path 84 .
  • the air that flows back through the gap flow path 84 contains a velocity component in the rotation direction of the fan 20 . Then, the air flowing through the gap flow paths 84 indicated by arrows F4 and F5 and the air flowing in from the first flow path 81 indicated by arrow F2 join in the second flow path 82, and then move toward the blades as indicated by arrow F3. It is sucked into the inter-blade passage 25 from the leading edge 26 side together with the main stream.
  • the pressure of the air flowing along the radially outer surface of the nozzle 60 is higher than the pressure of the main stream flowing into the fan 20 along the radially inner surface of the nozzle 60 . Therefore, the pressure difference between the pressure in the first flow path 81, the partition flow path 73 and the second flow path 82 and the pressure on the side of the air outlet 28 of the fan 20 becomes small, and the air outlet 28 side of the fan 20 increases the gap flow path. The amount of air flowing back through 84 can be reduced.
  • the main stream is sucked into the inter-blade passage 25 from the front edge 26 side of the fan 20 along the radially inner surface of the nozzle 60, as indicated by arrow F1 in FIG.
  • the air conditioner is set to the foot mode or the defroster mode
  • the pressure loss in the flow path on the downstream side of the blower 1 is greater than that in the face mode. Therefore, as the rotation speed of the fan 20 increases, the difference between the pressure on the side of the air outlet 28 of the fan 20 and the pressure on the side of the suction port 2 becomes larger than the pressure difference in the face mode.
  • the backflow air flows from the second flow path 82 through the partition flow path 73 and the first flow path 81 as indicated by the dashed arrow F6 in FIG. Then, it tries to flow inside the nozzle 60 across the end 61 of the nozzle 60 on the side opposite to the main plate.
  • the space between the nozzle 60 and the bell mouth 11 is partitioned into a plurality of partition channels 73 by a plurality of channel partition members 70, the backflow air passing through the partition channels 73 pressure loss increases, and the wind speed and volume of backflow air are reduced.
  • the inventor's research has revealed that the backflow air that tries to flow inside the nozzle 60 across the end 61 of the nozzle 60 on the side opposite to the main plate has a large wind speed distribution in the circumferential direction.
  • the space between the nozzle 60 and the bell mouth 11 is partitioned into a plurality of partitioned channels 73 by a plurality of channel partitioning members 70, the backflow air passing through the partitioned channels 73 pressure loss increases, and the circumferential wind velocity distribution of the backflow air is reduced.
  • the fan 1 of the sixth embodiment described above also reduces the wind speed and the air volume of the backflow air passing through the plurality of partition passages 73 in the same manner as the fan 1 described in the first embodiment and the like, and reduces the backflow across the nozzle 60. It is possible to reduce the circumferential wind velocity distribution of the air. Therefore, in the blower 1 of the sixth embodiment as well, the blowing efficiency can be improved and the noise can be reduced.
  • blower 1 was described as being used in a vehicle air conditioner, but the blower 1 is not limited to this, and can be used in various applications such as a ventilator or a blower. can.
  • the fan 20 included in the blower 1 was described as a turbo fan, but it is not limited to this, and may be a centrifugal fan such as a sirocco fan or a radial fan, for example.
  • the nozzle 60 provided in the blower 1 has a wing shape whose diameter decreases from one side to the other in the axial direction, and protrudes from the front wall 12 of the case 10 toward the side opposite to the main plate.
  • the nozzle 60 may have, for example, a simple cylindrical shape, or may not protrude from the front wall 12 of the case 10 toward the side opposite to the main plate.
  • the present disclosure is not limited to the above-described embodiments, and can be modified as appropriate. Moreover, the above-described embodiments are not unrelated to each other, and can be appropriately combined except when combination is clearly impossible. Further, in each of the above-described embodiments, it goes without saying that the elements constituting the embodiment are not necessarily essential, unless it is explicitly stated that they are essential, or they are clearly considered essential in principle. stomach. In addition, in each of the above-described embodiments, when numerical values such as the number, numerical value, amount, range, etc.

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

Abstract

Selon la présente invention, un boîtier (10) est doté d'une embouchure (11) dans laquelle est formé un orifice (2) d'aspiration servant à aspirer de l'air. Un ventilateur (20) comprend une plaque principale (21) qui est placée à l'intérieur du boîtier (10) et qui est capable de tourner autour d'un axe, une pluralité de pales (22) qui sont disposées autour de l'axe et liées à la plaque principale (21), et un carénage (30) qui est lié à des parties (23) de la pluralité de pales (22) qui sont situées sur les côtés à l'opposé de la plaque principale. Une buse (60) est formée sous une forme tubulaire et est placée dans une région radialement intérieure de l'embouchure (11). Des éléments (70) de séparation de trajets d'écoulement sont placés de façon intermittente dans la direction circonférentielle entre l'embouchure (11) et la buse (60), les éléments (70) de séparation de trajets d'écoulement séparant l'espace entre la buse (60) et l'embouchure (11) en une pluralité de trajets (73) d'écoulement séparés à travers lesquels s'écoule de l'air.
PCT/JP2022/006629 2021-03-10 2022-02-18 Soufflante WO2022190818A1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
JP2021-038408 2021-03-10
JP2021038408 2021-03-10
JP2021-190408 2021-11-24
JP2021190408A JP2022140271A (ja) 2021-03-10 2021-11-24 送風機

Publications (1)

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WO2022190818A1 true WO2022190818A1 (fr) 2022-09-15

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Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2013036444A (ja) * 2011-08-10 2013-02-21 Daikin Industries Ltd 遠心送風機
JP2016188578A (ja) * 2015-03-30 2016-11-04 パナソニックＩｐマネジメント株式会社 送風装置
JP2018109383A (ja) * 2017-01-04 2018-07-12 株式会社ヴァレオジャパン 遠心送風機
US10914316B1 (en) * 2011-08-23 2021-02-09 Climatecraft, Inc. Plenum fan

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2013036444A (ja) * 2011-08-10 2013-02-21 Daikin Industries Ltd 遠心送風機
US10914316B1 (en) * 2011-08-23 2021-02-09 Climatecraft, Inc. Plenum fan
JP2016188578A (ja) * 2015-03-30 2016-11-04 パナソニックＩｐマネジメント株式会社 送風装置
JP2018109383A (ja) * 2017-01-04 2018-07-12 株式会社ヴァレオジャパン 遠心送風機

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