WO2020008519A1 - Soufflante à aubes multiples et dispositif de climatisation - Google Patents

Soufflante à aubes multiples et dispositif de climatisation Download PDF

Info

Publication number
WO2020008519A1
WO2020008519A1 PCT/JP2018/025172 JP2018025172W WO2020008519A1 WO 2020008519 A1 WO2020008519 A1 WO 2020008519A1 JP 2018025172 W JP2018025172 W JP 2018025172W WO 2020008519 A1 WO2020008519 A1 WO 2020008519A1
Authority
WO
WIPO (PCT)
Prior art keywords
blade
impeller
rotation axis
air
blades
Prior art date
Application number
PCT/JP2018/025172
Other languages
English (en)
Japanese (ja)
Inventor
健一 迫田
一輝 岡本
菊地　仁
Original Assignee
三菱電機株式会社
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 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to PCT/JP2018/025172 priority Critical patent/WO2020008519A1/fr
Priority to JP2020528566A priority patent/JP6945739B2/ja
Priority to CN201880094504.0A priority patent/CN112352108B/zh
Publication of WO2020008519A1 publication Critical patent/WO2020008519A1/fr

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
    • F04D29/30—Vanes

Definitions

  • the present invention relates to a multi-blade blower with improved blowing performance and an air conditioner provided with the multi-blade blower.
  • the multi-blade blower includes a fan casing having an intake port and an exhaust port formed therein, and an impeller accommodated in the fan casing.
  • the multi-blade blower uses centrifugal force acting on air by a rotating impeller to pressurize air drawn into a fan casing from an intake port and discharge the air to the outside of the fan casing from an exhaust port.
  • the multi-blade blower is also called a sirocco fan.
  • the multi-blade blower is used, for example, as a blower of an air conditioner. Further, for example, a multi-blade blower is used for forcibly circulating air in a place where a static pressure is relatively high. The place where the static pressure is relatively high is, for example, a ventilation duct provided in a factory or a building, a floor under a house, or the like. Further, for example, a multi-blade blower is also used as a device for ventilating a room such as a kitchen or a kitchen.
  • the impeller of the multi-blade blower rotates around the rotation axis.
  • This impeller includes a main plate and a plurality of blades extending in the rotation axis direction from the vicinity of the outer edge of the main plate. These blades are arranged at intervals on a circle about the rotation axis. Specifically, each of the blades has a first end that is one end in the direction of the rotation axis and a second end that is the other end in the direction of the rotation axis. Each of the blades has a first end connected to the main plate. The second ends of the blades are opposed to the intake ports of the fan casing.
  • the air sucked into the fan casing from the intake port is surrounded by the plurality of blades and the main plate of the impeller from the second end side on the suction side. Flows into the space. Then, the air that has flowed into the space surrounded by the plurality of blades and the main plate is compressed by a centrifugal force in a substantially radial direction to the outside of the impeller and sent out from between adjacent blades. Thereafter, the air flowing out of the impeller is discharged from the exhaust port to the outside of the fan casing.
  • the radial direction is a direction extending from the rotation axis in a direction perpendicular to the rotation axis.
  • the flow velocity of the air flowing between the adjacent blades differs in the rotation axis direction. Specifically, the flow velocity of the air flowing between the adjacent blades is higher on the main plate side and lower on the second end side, which is the suction side.
  • the air flowing between the adjacent blades on the second end side on the suction side is the diameter of the impeller so that the air flowing into the space surrounded by the plurality of blades and the main plate flows between the adjacent blades. Due to the inertial force acting when turning in the direction, it does not flow perpendicular to the rotation axis. That is, the air flowing between the adjacent blades on the second end side that is the suction side has a flow inclined toward the main plate with respect to the direction perpendicular to the rotation axis. As described above, the flow rate of the air flowing between the adjacent blades is not uniform in the direction of the rotation axis, and also the velocity in the direction perpendicular to the rotation axis is not uniform.
  • the blades of an impeller are usually designed assuming a flow having a uniform velocity distribution between adjacent blades. Therefore, near the second end side on the suction side, the flow assumed in the design differs from the actual flow. Therefore, the pressure loss of the air passing between the adjacent blades is large near the second end side on the suction side. Further, due to the non-uniform air flow flowing between the adjacent blades, the air flow flowing out between the adjacent blades also has a velocity distribution in the rotation axis direction. Then, a swirling flow is generated inside the fan casing due to the speed distribution, so that the blowing performance of the multi-blade blower is deteriorated.
  • the distance from the rotating shaft of the impeller to the inner peripheral end of the blade is set. Is changed in the direction of the rotation axis, and the distance from the rotation axis of the impeller to the outer peripheral end of the blade is changed in the direction of the rotation axis (for example, see Patent Document 1).
  • the multi-blade blower described in Patent Document 1 passes between adjacent blades by changing the distance from the rotating shaft to the inner peripheral end of the blade and the distance from the rotating shaft to the outer peripheral end of the blade in the direction of the rotating shaft.
  • the blade shape is adapted to the air flow.
  • the multi-blade blower described in Patent Literature 1 aims to suppress the pressure loss of air passing between adjacent blades.
  • simply changing the distance from the rotating shaft to the inner peripheral end of the blade and the distance from the rotating shaft to the outer peripheral end of the blade in the direction of the rotating shaft does not reduce the pressure loss of air as a whole multi-blade blower. small.
  • the present invention has been made in order to solve the above-described problems, and to obtain a multi-blade blower that can reduce the pressure loss of air of the entire multi-blade blower as compared with the related art and improve the blowing performance.
  • a second object of the present invention is to obtain an air conditioner provided with such a multi-blade blower.
  • the multi-blade blower according to the present invention has a fan casing having an intake port and an exhaust port formed therein, and is housed in the fan casing, and rotates around a rotation axis to flow into the fan casing from the intake port.
  • An impeller that generates a flow of air flowing out of the fan casing from the exhaust port, the impeller extends along the rotation axis, and has an interval on a circle centered on the rotation axis.
  • the entrance angle is the first intermediate portion From the second end to the second end, and in a cross section perpendicular to the rotation axis, an intersection between the outer peripheral end and the pressure surface is a first point, and an intersection between the outer peripheral end and the suction surface is a first point.
  • the air conditioner according to the present invention includes the multiblade blower according to the present invention, and a heat exchanger that heats or cools the air supplied by the multiblade blower.
  • the multiblade blower according to the present invention can suppress the pressure loss of the air passing between the adjacent blades, and can also suppress the generation of a vortex in the airflow between the impeller and the exhaust port. For this reason, the multi-blade blower according to the present invention can reduce the pressure loss of the air of the entire multi-blade blower as compared with the related art, and can improve the blowing performance.
  • FIG. 1 is a perspective view showing a multi-blade blower according to Embodiment 1 of the present invention.
  • FIG. 2 is a plan view showing a state where a top plate of a casing is removed in the multi-blade blower according to Embodiment 1 of the present invention. It is a perspective view which shows the impeller of the multi-blade fan which concerns on Embodiment 1 of this invention.
  • FIG. 3 is a diagram in which the impeller according to Embodiment 1 of the present invention is cut along a plane including a rotation axis of the impeller, and the blade is observed in a direction perpendicular to the plane.
  • FIG. 13 is a refrigerant circuit diagram illustrating an example of an air-conditioning apparatus according to Embodiment 6 of the present invention.
  • FIG. 1 is a perspective view showing a multi-blade blower according to Embodiment 1 of the present invention.
  • FIG. 2 is a plan view showing the multi-blade blower according to Embodiment 1 of the present invention in a state where an upper plate of a casing is removed.
  • FIG. 3 is a perspective view showing an impeller of the multi-blade blower according to Embodiment 1 of the present invention.
  • the arc-shaped arrows shown in FIGS. 2 and 3 indicate the rotation direction of the impeller 30.
  • the multi-blade blower 100 is a device for forcibly flowing air by pressurizing air taken in from the intake port 2 and discharging the air from the exhaust port 4.
  • the multi-blade blower 100 includes a fan casing 1 in which an intake port 2 and an exhaust port 4 are formed, and an impeller 30 housed in the fan casing 1.
  • the impeller 30 is rotated about the rotation shaft 31 by the rotation of a driving device 70 such as a motor, and is a component that forcibly sends air to the outside of the impeller 30 in a substantially radial direction by centrifugal force generated by the rotation. It is.
  • the radial direction is a direction extending from the rotation shaft 31 in a direction perpendicular to the rotation shaft 31. That is, the impeller 30 rotates around the rotation shaft 31 to generate a flow of air flowing into the fan casing 1 from the intake port 2 and flowing out of the fan casing 1 from the exhaust port 4.
  • the impeller 30 includes a main plate 40 and a plurality of blades 50.
  • the main plate 40 is a disk provided to be rotatable about the rotation shaft 31.
  • the main plate 40 is provided with a plurality of blades 50. More specifically, the main plate 40 includes a first surface 41 and a second surface 42 which is a back surface of the first surface 41. In the first embodiment, a plurality of blades 50 are provided on the first surface 41 of the main plate 40. The plurality of blades 50 are provided, for example, near the outer peripheral edge of the main plate 40.
  • the plurality of blades 50 extend from the main plate 40 along the rotation axis 31.
  • the plurality of blades 50 are arranged at intervals on a circle centered on the rotation shaft 31. More specifically, each of the blades 50 includes a first end 51 that is one of the ends in the direction of the rotation shaft 31 and a second end 52 that is the other end of the end in the direction of the rotation shaft 31.
  • Each first end 51 of the blade 50 is connected to the first surface 41 of the main plate 40.
  • each second end 52 of the blade 50 faces the intake port 2 of the fan casing 1. That is, each blade 50 extends substantially perpendicularly to the first surface 41 of the main plate 40 in a direction from the first surface 41 of the main plate 40 toward the intake port 2.
  • Each blade 50 is inclined parallel to the radial direction or at a predetermined angle with respect to the radial direction when observed in the direction of the rotating shaft 31.
  • the direction of the rotation shaft 31 is a direction in which the rotation shaft 31 extends.
  • the connecting portion 45 is a series of annular members having a diameter capable of connecting the second ends 52 of the plurality of blades 50. With this connection, the positional relationship between the second ends 52 of the plurality of blades 50 is maintained, and the plurality of blades 50 are reinforced.
  • the connecting portion 45 may be an annular plate member having a width capable of covering the second end 52 of each blade 50, or may be an annular member connecting the outer peripheral sides of each blade 50.
  • the fan casing 1 is a scroll type fan casing.
  • the fan casing 1 includes a main body 10 that accommodates the impeller 30 and a duct 20 that is connected to the main body 10.
  • the main body 10 is, for example, a hollow cylindrical component having a substantially cylindrical space formed therein.
  • the main body 10 generally surrounds the entire impeller 30.
  • the shape of the space formed inside the fan casing 1 is not limited to a columnar shape, and may be, for example, a columnar shape having a polygonal cross section.
  • the fan casing 1 includes a lower surface plate 11, an upper surface plate 12, and a peripheral wall 13 as members constituting a wall surface.
  • the upper surface plate 12 has an inlet 2 formed in a region facing the second end 52 of the plurality of blades 50 so that air can flow between the impeller 30 and the outside of the fan casing 1.
  • a bell mouth 3 is provided in the intake port 2.
  • the bell mouth 3 has a gradually decreasing cross section from the outside to the inside of the fan casing 1 in order to allow air to flow smoothly in and around the intake port 2.
  • the center of the intake port 2 and the rotating shaft 31 of the impeller 30 substantially coincide with each other.
  • the lower plate 11 is disposed to face the upper plate 12 in the direction of the rotation axis 31. That is, the upper surface plate 12 is provided on the second end 52 side, which is the intake side of the impeller 30, and the lower surface plate 11 is provided on the main plate 40 side of the impeller 30.
  • the peripheral wall 13 connects the outer edge of the lower surface plate 11 and the outer edge of the upper surface plate 12, and extends to the outer peripheral side of the impeller 30.
  • the gap between the peripheral wall 13 of the main body 10 and the outer peripheral end of the impeller 30 expands at a predetermined rate in the direction of rotation of the impeller 30 from a tongue 26 described below.
  • the air sent from the impeller 30 can flow smoothly through the gap.
  • the flow area of the air gradually increases from the tongue portion 26 to the main body exhaust port 14, the static pressure of the air efficiently increases as the air sent from the impeller 30 flows through the gap. Can be.
  • the duct section 20 is a hollow tube having a substantially rectangular cross section orthogonal to the flow direction of air.
  • the duct part 20 constitutes a flow path for guiding the air flowing out of the main body part exhaust port 14 of the main body part 10 to the outside of the fan casing 1.
  • An opening at one end of the duct portion 20 is an inlet 25 through which air flowing into the duct portion 20 passes.
  • the opening at the other end of the duct section 20 is an exhaust port 4 through which air flowing out of the duct section 20 passes, in other words, air exhausted from the fan casing 1. That is, the periphery of the inflow port 25 of the duct section 20 is connected to the periphery of the main body exhaust port 14 of the main body 10.
  • the duct unit 20 includes an extension plate 21, a diffuser plate 22, a lower plate 23, and an upper plate 24 as members constituting a wall surface.
  • the extension plate 21 is smoothly connected to an end of the peripheral wall 13 of the main body 10 that forms a peripheral edge of the main body exhaust port 14 on the downstream side in the air flow direction.
  • the diffuser plate 22 is connected to an end of the peripheral wall 13 of the main body 10 that constitutes the peripheral edge of the main body exhaust port 14 on the upstream side in the air flow direction.
  • the diffuser plate 22 is disposed at a predetermined angle with the extension plate 21 such that the cross-sectional area of the flow path gradually increases in the direction of air flow in the duct portion 20.
  • the lower plate 23 and the upper plate 24 connect the outer edge of the extension plate 21 and the outer edge of the diffuser plate 22, respectively, and form a substantially rectangular flow path. Further, the lower surface plate 23 is connected to an end of the lower surface plate 11 of the main body 10 that constitutes a peripheral edge of the main body exhaust port 14. The upper surface plate 24 is connected to an end of the upper surface plate 12 of the main body 10 that forms a peripheral edge of the main body exhaust port 14.
  • the connection between the diffuser plate 22 and the peripheral wall 13 of the main body 10 is smoothly connected from the lower surface plate 11 to the upper surface plate 12 of the fan casing 1 with a predetermined radius of curvature, and forms a tongue 26.
  • the tongue 26 is a branch point when the flow that has flowed into the main body 10 through the impeller 30 from the air inlet 2 is collected by the main body 10, and the collected air flows into the duct 20. . That is, the static pressure of the air flowing into the duct portion 20 increases while passing through the main body portion 10, and becomes higher than the vicinity of the tongue portion 26 in the main body portion 10. Due to this pressure difference, the tongue portion 26 has a function of partitioning the flow of air flowing again from the duct portion 20 into the main body portion 10.
  • the tongue portion 26 is formed with a predetermined radius of curvature, even when air collides with the tongue portion 26 when air flows from the main body portion 10 into the duct portion 20, the tongue portion 26 is generated. Disturbance can be reduced. For this reason, it is possible to suppress the deterioration of the blowing performance and the increase in noise.
  • the radius of curvature of the tongue 26 is constant in the direction of the rotation axis 31, but the radius of curvature of the tongue 26 does not need to be constant in the direction of the rotation axis 31.
  • the radius of curvature of the tongue 26 on the intake port 2 side, that is, the upper surface plate 12 side may be larger than the radius of curvature of the tongue portion 26 on the lower surface plate 11 side.
  • FIGS. 4 to 7 show the shape of one blade 50.
  • FIG. 4 is a diagram in which the impeller according to Embodiment 1 of the present invention is cut along a plane including the rotation axis of the impeller, and the blade is observed in a direction perpendicular to the plane.
  • FIGS. 5 to 7 are views showing the shape of the blade of the impeller according to Embodiment 1 of the present invention when observed in the rotation axis direction of the impeller.
  • FIGS. 5 to 7 are diagrams in which the shape of the blade 50 is observed in a cross section perpendicular to the rotation shaft 31.
  • FIG. 5 shows the shape of the blade 50 at the position of the first end 51 which is the end on the main plate 40 side.
  • FIG. 5 shows the shape of the blade 50 at the position of the first end 51 which is the end on the main plate 40 side.
  • FIG. 6 shows the shape of the blade 50 at the position of the second end 52 which is the end on the intake port 2 side.
  • FIG. 7 shows the shape of the blade 50 at the position of the first end 51 and the shape of the blade 50 at the position of the second end 52.
  • the shape of the blade 50 at the position of the second end 52 is set to facilitate the distinction between the shape of the blade 50 at the position of the first end 51 and the shape of the blade 50 at the position of the second end 52. Is indicated by a broken line. 5 to 7 indicate the rotation direction of the impeller 30.
  • the blade 50 has a pressure surface 55, a suction surface 56, an inner peripheral end 53, and an outer peripheral end 54.
  • the positive pressure surface 55 is a front surface in the rotation direction of the impeller 30.
  • the negative pressure surface 56 is a surface on the rear side in the rotation direction of the impeller 30.
  • the inner peripheral end 53 is a radial end extending in a direction perpendicular to the rotating shaft 31 from the rotating shaft 31, and is an end closer to the rotating shaft 31.
  • the outer peripheral end 54 is an end in the radial direction, and is an end farther from the rotation shaft 31.
  • the length of the blade 50 in the direction of the rotation axis 31 is the length L1. That is, the length from the first end 51 to the second end 52 in the direction of the rotation shaft 31 is the length L1.
  • the distance between the rotating shaft 31 and the outer peripheral end 54 of the blade 50 is the same distance Do from the first end 51 to the second end 52.
  • the distance between the rotating shaft 31 and the inner peripheral end 53 of the blade 50 is the same distance Di0 from the first end 51 to the first intermediate portion 57.
  • the distance between the rotating shaft 31 and the inner peripheral end 53 of the blade 50 gradually increases from the first intermediate portion 57 toward the second end 52, and becomes the distance Di1 at the position of the second end 52.
  • the first intermediate portion 57 is located between the first end 51 and the second end 52, and is located at a length L0 from the first end 51 in the first embodiment.
  • the length L0 is, for example, approximately half the length of the length L1.
  • “same” referred to in the first embodiment does not mean exactly the same, but means substantially the same.
  • the distance between the rotating shaft 31 and the outer peripheral end 54 of the blade 50 is designed to be the same distance Do from the first end 51 to the second end 52.
  • the distance between the rotating shaft 31 and the outer peripheral end 54 of the blade 50 does not become exactly the same distance Do from the first end 51 to the second end 52, and a processing error or the like.
  • the distance between the rotary shaft 31 and the outer peripheral end 54 of the blade 50 from the first end 51 to the second end 52 is increased.
  • the same distance Do are referred to as the same distance Do.
  • the center line 60 of the blade 50 has a shape in which arcs having a plurality of radii of curvature are connected. Note that the center line 60 is a line connecting points at the same distance from the positive pressure surface 55 and the negative pressure surface 56 from the inner peripheral end 53 to the outer peripheral end 54.
  • the entrance angle of the blade 50 is the same entrance angle ⁇ 0 from the first end 51 to the first intermediate portion 57.
  • the entrance angle of the blade 50 gradually increases from the first intermediate portion 57 toward the second end 52, and at the position of the second end 52, the entrance angle ⁇ 1. That is, ⁇ 1> ⁇ 0.
  • the entrance angle of the blade 50 is defined as follows. First, in a cross section perpendicular to the rotation axis 31, an arc is drawn centering on the rotation axis 31 and passing through the intersection of the center line 60 and the inner peripheral end 53. This arc is defined as an inner circumferential arc.
  • a tangent line of the inner circumference side arc at the intersection of the center line 60 and the inner circumference end 53 is drawn so as to extend in a direction opposite to the rotation direction of the impeller 30.
  • a tangent to the center line 60 at the intersection of the center line 60 and the inner peripheral end 53 is drawn so as to extend in a direction opposite to the rotation direction of the impeller 30.
  • the exit angle of the blade 50 is the same exit angle ⁇ from the first end 51 to the second end 52.
  • the exit angle of the blade 50 is defined as follows. First, in a cross section perpendicular to the rotation axis 31, an arc is drawn centering on the rotation axis 31 and passing through the intersection of the center line 60 and the outer peripheral end 54. This arc is defined as an outer peripheral arc. In addition, a tangent to the outer circumferential side arc at the intersection of the center line 60 and the outer circumferential end 54 is drawn so as to extend in a direction opposite to the rotation direction of the impeller 30.
  • a tangent to the center line 60 at the intersection of the center line 60 and the outer peripheral end 54 is drawn so as to extend in the rotation direction of the impeller 30.
  • the angle between the tangent to the outer peripheral arc and the tangent to the center line 60 is the exit angle of the blade 50.
  • the outer peripheral end 54 of the blade 50 is arranged at the following position. Specifically, in a cross section perpendicular to the rotation axis 31, the first point 61, the second point 62, the third point 63, the first straight line 65, and the second straight line 66 are defined as follows.
  • the intersection between the outer peripheral end 54 and the pressure surface 55 is referred to as a first point 61.
  • the intersection between the outer peripheral end 54 and the negative pressure surface 56 is defined as a second point 62.
  • the intersection between the outer peripheral end 54 and the center line 60 of the blade 50 is defined as a third point 63.
  • a virtual straight line connecting the first point 61 at the first end 51 and the rotation axis 31 is defined as a first straight line 65.
  • a virtual straight line connecting the second point 62 at the first end 51 and the rotation axis 31 is defined as a second straight line 66.
  • the third point 63 from the first end 51 to the second end 52 is located between the first straight line 65 and the second straight line 66.
  • the outer peripheral end 54 of the blade 50 By arranging the outer peripheral end 54 of the blade 50 from the first end 51 to the second end 52 in this manner, the outer peripheral end 54 of the blade 50 can be radially moved, as can be seen from, for example, a region A shown in FIG. When observed, the outer peripheral end 54 has a substantially linear shape substantially parallel to the rotating shaft 31.
  • the air sucked into the impeller 30 from the intake port 2 in the direction of the rotation shaft 31 changes its flow direction in the radial direction from the direction of the rotation shaft 31 by the centrifugal force generated by the rotation of the impeller 30. .
  • the air sucked into the impeller 30 does not suddenly change its flow direction on the second end 52 side, which is the intake port 2 side of the impeller 30. Therefore, the flow on the second end 52 side of the impeller 30 becomes a flow inclined in the direction of the main plate 40 with respect to the direction perpendicular to the rotation shaft 31.
  • the flow rate of the air passing through the second end 52 of the impeller 30 is smaller than that of the main plate 40. That is, on the side of the second end 52 of the impeller 30, the velocity of the air at the inner peripheral end 53 of the blade 50 is small. Therefore, it is difficult for air to flow between the adjacent blades 50 on the second end 52 side of the impeller 30.
  • the distance between the rotating shaft 31 and the inner peripheral end 53 of the blade 50 is from the first intermediate portion 57 to the second end 52 on the intake port 2 side. It is getting larger gradually. Therefore, the inner peripheral end 53 of the blade 50 on the second end 52 side can be directly opposed to the flow inclined in the direction of the main plate 40. Therefore, air easily flows between the adjacent blades 50 on the second end 52 side.
  • the entrance angle of the blade 50 gradually increases from the first intermediate portion 57 to the second end 52 on the intake port 2 side.
  • the air that is about to flow radially between the adjacent blades 50 collides with the negative pressure surface 56 of the blade 50 when the entrance angle of the blade 50 is small.
  • the vicinity of the inner peripheral end 53 becomes nearly parallel to the air that is about to flow radially between the adjacent blades 50. Therefore, by increasing the entrance angle of the blade 50, it is possible to suppress the air flowing between the adjacent blades 50 from colliding with the negative pressure surface 56 of the blade 50.
  • impeller 30 according to the first embodiment can reduce pressure loss generated near second end 52 of blade 50.
  • the outer peripheral end 54 of the blade 50 according to the first embodiment has a substantially linear shape substantially parallel to the rotating shaft 31.
  • the flow of the air sent from the space between the adjacent blades 50 into the main body 10 has a small inclination with respect to the direction perpendicular to the rotation shaft 31. Therefore, in the multi-blade blower 100 according to the first embodiment, the flow of air between the impeller 30 and the exhaust port 4 in the fan casing 1 is caused by the lower plate 11, the upper plate 12, the lower plate 23, and the upper plate 24. Collision can be suppressed.
  • the multi-blade blower 100 it is possible to suppress the occurrence of a vortex in the flow of air between the impeller 30 and the exhaust port 4 in the fan casing 1, and to suppress the occurrence of a vortex in the location. Pressure loss can be reduced.
  • the distance between the rotating shaft 31 and the inner peripheral end 53 is from the first intermediate portion 57 to the second end 52.
  • the entrance angle gradually increases toward the second end 52 from the first intermediate portion 57.
  • the third point 63 from the first end 51 to the second end 52 is , Between the first straight line 65 and the second straight line 66.
  • the multi-blade blower 100 according to the first embodiment can suppress the pressure loss of the air passing between the adjacent blades 50, and the vortex flows in the air flow between the impeller 30 and the exhaust port 4. The occurrence can also be suppressed.
  • the multi-blade fan 100 according to Embodiment 1 can reduce the pressure loss of the air of the entire multi-blade fan 100 as compared with the related art, and can improve the blowing performance.
  • the multi-blade blower 100 according to the first embodiment can reduce the pressure loss of the air of the entire multi-blade blower 100 as compared with the related art, so that the effect of reducing noise can be obtained.
  • the length L0 from the first end 51 indicating the position of the first intermediate portion 57 of the blade 50 is in the range of 0.5 ⁇ L0 / L1 ⁇ 0.7.
  • the inventors used a conventional impeller in which the distance between the rotary shaft 31 and the inner peripheral end 53 of the blade 50 and the inlet angle did not change from the first end 51 to the second end 52, and used the rotary shaft 31 In the direction, the change in the flow velocity of the air flowing between the adjacent blades 50 was examined. As a result, it was confirmed that the flow velocity of the air gradually decreased from the substantially center position of the blade 50 in the direction of the rotation shaft 31 toward the second end 52.
  • the distance between the rotary shaft 31 and the inner peripheral end 53 of the blade 50 and the inlet angle are not changed.
  • the distance and the inlet angle between the rotating shaft 31 and the inner peripheral end 53 of the blade 50 are set as described above so that the air can easily flow between the adjacent blades 50.
  • the length L0 from the first end 51 indicating the position of the first intermediate portion 57 of the blade 50 is preferably in a range of 0.5 ⁇ L0 / L1 ⁇ 0.7.
  • the distance between the rotary shaft 31 and the inner peripheral end 53 of the blade 50 and the change in the inlet angle between the first intermediate portion 57 and the second end 52 may change linearly, It may change quadratically.
  • Embodiment 2 From the first end 51 to the second end 52, the distance between the rotating shaft 31 and the outer peripheral end 54 of the blade 50 may be varied as follows.
  • items that are not particularly described are the same as those in the first embodiment, and the same functions and configurations are described using the same reference numerals.
  • FIG. 8 is a perspective view showing an impeller of a multi-blade blower according to Embodiment 2 of the present invention.
  • FIG. 9 is a diagram in which the impeller according to Embodiment 2 of the present invention is cut along a plane including the rotation axis of the impeller, and the blade is observed in a direction perpendicular to the plane.
  • FIG. 10 is a diagram illustrating a shape of the blade of the impeller according to Embodiment 2 of the present invention when observed in the rotation axis direction of the impeller.
  • FIG. 10 is a diagram in which the shape of the blade 50 is observed in a cross section perpendicular to the rotation shaft 31.
  • FIG. 10 is a diagram in which the shape of the blade 50 is observed in a cross section perpendicular to the rotation shaft 31.
  • FIG. 10 shows the shape of the blade 50 at the position of the first end 51 and the shape of the blade 50 at the position of the second end 52.
  • the shape of the blade 50 at the position of the second end 52 is set to facilitate the distinction between the shape of the blade 50 at the position of the first end 51 and the shape of the blade 50 at the position of the second end 52. Is indicated by a broken line.
  • An arc-shaped arrow shown in FIG. 8 and a white arrow shown in FIG. 10 indicate the rotation direction of the impeller 30.
  • the distance between the rotating shaft 31 and the outer peripheral end 54 of the blade 50 is the same distance Do0 from the first end 51 to the second intermediate portion 58.
  • the distance between the rotating shaft 31 and the outer peripheral end 54 of the blade 50 gradually increases from the second intermediate portion 58 toward the second end 52, and becomes the distance Do1 at the position of the second end 52.
  • the second intermediate portion 58 is located between the first end 51 and the second end 52, and is located at a position of a length L0 from the first end 51 in the second embodiment.
  • the length L0 is, for example, approximately half the length of the length L1. Note that the length from the first end 51 to the first intermediate portion 57 may be different from the length from the first end 51 to the second intermediate portion 58.
  • the exit angle of the blade 50 is the same exit angle ⁇ 0 from the first end 51 to the second intermediate portion 58.
  • the exit angle of the blade 50 gradually decreases from the second intermediate portion 58 toward the second end 52, and at the position of the second end 52, the exit angle is ⁇ 1. That is, ⁇ 1 ⁇ 0. Note that the change in the exit angle between the second intermediate portion 58 and the second end 52 may change linearly or may change quadratically.
  • the third point 63 from the first end 51 to the second end 52 is located between the first straight line 65 and the second straight line 66.
  • the flow of air when the multi-blade blower 100 according to Embodiment 2 is in operation will be described.
  • the impeller 30 rotates, the air inside the impeller 30 is sent out of the impeller 30 in a substantially radial direction by centrifugal force generated by the rotation of the impeller 30. Further, air flows into the impeller 30 from the intake port 2.
  • the generated centrifugal force increases as the outer diameter of the impeller 30 increases.
  • the outer diameter of the impeller 30 is closer to the second end 52 closer to the intake port 2 where the flow velocity of the air is slow and the air is inclined with respect to the rotation shaft 31 and the air easily flows. Becomes larger. Therefore, the centrifugal force generated in the air sucked into the impeller 30 increases toward the second end 52 closer to the intake port 2.
  • the flow of air passing through the second end 52 of the blade 50 on the intake port 2 side flows more radially outward of the impeller 30 due to the strong centrifugal force. Further, the flow of air is pulled outward in the radial direction of the impeller 30 by the strong centrifugal force, so that the flow inclined with respect to the direction perpendicular to the rotation axis 31 becomes more perpendicular to the rotation axis 31. It becomes easy to flow toward. That is, the difference between the flow velocity of the air flowing out of the impeller 30 from the first end 51 side and the flow velocity of the air flowing out of the impeller 30 from the second end 52 side becomes small, and the rotating shaft 31 The velocity distribution in the direction is reduced.
  • the multi-blade blower 100 according to the second embodiment Since the velocity distribution in the direction of the rotating shaft 31 is relaxed, the flow of the air sent from the impeller 30 has a smaller inclination with respect to the direction perpendicular to the rotating shaft 31 than in the first embodiment. For this reason, in the multi-blade blower 100 according to the second embodiment, the flow of air between the impeller 30 and the exhaust port 4 in the fan casing 1 is lower than that of the first embodiment. Further, collision with the lower plate 23 and the upper plate 24 can be further suppressed. For this reason, in the multi-blade blower 100 according to the second embodiment, a vortex flow is generated in the air flow between the impeller 30 and the exhaust port 4 in the fan casing 1 as compared with the first embodiment. It can be further suppressed, and the pressure loss at the location can be further reduced. That is, the multi-blade blower 100 according to Embodiment 2 further improves the blowing performance.
  • the exit angle of the blade 50 is set to the second intermediate portion. From 58 toward the second end 52, it gradually decreases. Therefore, the air flowing out of the impeller 30 from the second end 52 side flows out of the impeller 30 as compared with the air flowing out of the impeller 30 from the first end 51 side. Easier to do. Thereby, the velocity distribution in the direction of the rotating shaft 31 is further reduced, and the blowing performance is further improved.
  • the length L0 from the first end 51 indicating the position of the second intermediate portion 58 of the blade 50 is in the range of 0.5 ⁇ L0 / L1 ⁇ 0.7 as described in the first embodiment. Is preferred.
  • Embodiment 3 From the first end 51 to the second end 52, the inner peripheral end 53 of the blade 50 may be arranged as follows.
  • items that are not particularly described are the same as those in the first or second embodiment, and the same functions and configurations are described using the same reference numerals.
  • an example will be described in which the arrangement of the inner peripheral end 53 of the blade 50 is modified with respect to the impeller 30 described in the second embodiment.
  • FIG. 11 is a diagram showing a shape of the blade of the impeller according to Embodiment 3 of the present invention when observed in the rotation axis direction of the impeller.
  • FIG. 11 is a diagram in which the shape of the blade 50 is observed in a cross section perpendicular to the rotation shaft 31.
  • FIG. 11 shows the shape of the blade 50 at the position of the first end 51 and the shape of the blade 50 at the position of the second end 52.
  • the white arrows shown in FIG. 11 indicate the rotation direction of the impeller 30.
  • the inner peripheral end 53 of the blade 50 gradually moves from the first intermediate portion 57 to the second end 52 on the side opposite to the rotation direction of the blade 50. Has receded. Further, in the third embodiment, when the same blade 50 is observed in the direction of the rotation shaft 31, a cross section of the blade 50 at the position where the inner peripheral end 53 is the first end 51 from the first end 51 to the second end 52. And overlap. In order to arrange the inner peripheral end 53 in this manner, specifically, in the third embodiment, the blade 50 has the following shape.
  • the center line 60 of the blade 50 has a shape in which arcs having a plurality of radii of curvature are connected.
  • an arc passing through the inner peripheral end 53 of the plurality of arcs of the center line 60 has the same center and the same radius of curvature.
  • the inner peripheral end 53 of the blade 50 gradually recedes from the first intermediate portion 57 toward the second end 52 in a direction opposite to the rotation direction of the blade 50.
  • the inner peripheral end 53 overlaps the cross section of the blade 50 at the position of the first end 51 from the first end 51 to the second end 52.
  • the inner peripheral end 53 By arranging the inner peripheral end 53 in such a manner, the vicinity of the inner peripheral end 53 becomes almost parallel to the air that is about to flow radially between the adjacent blades 50. Therefore, it is possible to suppress the air flowing between the adjacent blades 50 from colliding with the negative pressure surface 56 of the blade 50. Therefore, air easily flows between the adjacent blades 50 on the second end 52 side, and the pressure loss generated near the second end 52 of the blade 50 can be reduced.
  • the inner peripheral end 53 in such a manner, when the same blade 50 is observed in the direction of the rotation shaft 31, the inner peripheral end 53 becomes the first end 51 from the first end 51 to the second end 52. Since it overlaps with the cross section of the blade 50 at the position, when the impeller 30 is manufactured by injection molding, the vicinity of the inner peripheral end 53 of the blade 50 can be molded by a mold that moves in the direction of the rotation shaft 31. Therefore, by arranging the inner peripheral end 53 in such a manner, when the impeller 30 is manufactured by injection molding, the manufacture of the impeller 30 becomes easy.
  • FIG. 12 is a diagram showing a measurement result of a static pressure rise amount in the multi-blade blower 100 according to Embodiment 3 of the present invention.
  • FIG. 13 is a diagram showing a measurement result of the blowing efficiency in the multi-blade blower 100 according to Embodiment 3 of the present invention.
  • 12 and 13 show the measurement results of the multiblade blower 100 according to the third embodiment.
  • the black circles in FIGS. 12 and 13 indicate the measurement results of the conventional multi-blade fan.
  • each blade 50 is changed from the first end 51 to the second end 52 to a blade whose cross section perpendicular to the rotation shaft 31 does not change from the multi-blade blower 100 according to the third embodiment.
  • a modified multi-blade blower was used. As can be seen from FIGS. 12 and 13, the multi-blade blower 100 according to Embodiment 3 of the present invention has higher static pressure and blowing efficiency than the conventional multi-blade blower, and the improvement of the blowing performance is recognized. Can be
  • Embodiment 4 With respect to the multi-blade blower 100 described in the first to third embodiments, the main plate 40 of the impeller 30 is cut out as described below, so that the impeller 30 can be easily manufactured.
  • items that are not particularly described are the same as those in any of the first to third embodiments, and the same functions and configurations are described using the same reference numerals.
  • an example in which the main plate 40 of the impeller 30 shown in the third embodiment is cut away will be described.
  • FIG. 14 is a diagram in which a part of the main plate of the impeller according to Embodiment 4 of the present invention is observed in the rotation axis direction.
  • FIG. 14 also shows the shape of the blade 50 at the positions of the first end 51 and the second end 52.
  • the shape of the blade 50 at the position of the second end 52 is set to facilitate the distinction between the shape of the blade 50 at the position of the first end 51 and the shape of the blade 50 at the position of the second end 52. Is indicated by a broken line. 14 indicate the rotation direction of the impeller 30.
  • the main plate 40 of the impeller 30 has a cutout projection area 43 in which the blade 50 is projected onto the main plate 40 in the direction of the rotation axis 31.
  • the range indicated by hatching in FIG. 14 is the projection range 43.
  • the main plate 40 of the impeller 30 is notched in a range indicated by hatching in FIG.
  • the main plate 40 may have a cutout area larger than the projection range 43 as long as the entire cutout area includes the entire projection range 43.
  • the main plate 40 as in the fourth embodiment By cutting the main plate 40 as in the fourth embodiment, when the impeller 30 is manufactured by injection molding, the portion of the die where the negative pressure surface 56 side of the blade 50 is molded is cut out of the main plate 40. Can be inserted from the point. Therefore, by cutting out main plate 40 as in the fourth embodiment, impeller 30 can be manufactured using a pair of dies that move in the direction of rotation shaft 31. Therefore, by cutting the main plate 40 as in the fourth embodiment, the manufacture of the impeller 30 becomes easier as compared with the case where the main plate 40 is not cut.
  • the cutout portion of the main plate 40 is on the negative pressure side of the blade 50.
  • the pressure on the suction side of the blade 50 is lower than the pressure on the pressure side of the blade 50. For this reason, even if main plate 40 is cut off as in the fourth embodiment, a decrease in the blowing performance of multi-blade blower 100 can be suppressed to a small level.
  • Embodiment 5 FIG.
  • the multi-blade blower 100 described in the first to fourth embodiments is a so-called single-suction type multi-blade blower.
  • the present invention is not limited to this, and a plurality of blades 50 may be connected to both the first surface 41 and the second surface 42 of the main plate 40 shown in the first to fourth embodiments.
  • the multi-blade fan 100 may be configured as a so-called double suction type multi-blade fan.
  • items that are not particularly described are the same as those in any of the first to fourth embodiments, and the same functions and configurations are described using the same reference numerals.
  • FIG. 15 is a cross-sectional view showing a main part of a multi-blade blower according to Embodiment 5 of the present invention.
  • FIG. 15 is a view in which the multi-blade blower 100 is cut along a plane including the rotation shaft 31, and shows a part of the impeller 30 and a part of the fan casing 1 near the impeller 30.
  • the impeller 30 according to the fifth embodiment a plurality of blades 50 are connected to both the first surface 41 and the second surface 42 of the main plate 40.
  • the intake port 2 is formed in the lower surface plate 11 of the fan casing 1 at a position facing the second ends 52 of the plurality of blades 50 provided on the second surface 42. That is, the multi-blade blower 100 according to Embodiment 5 is a so-called double-suction type multi-blade blower.
  • the effects shown in the first to fourth embodiments can be obtained.
  • a plurality of conventional blades may be provided on one of the first surface 41 and the second surface 42. If the plurality of blades 50 described in the first to fourth embodiments are provided on the other of the first surface 41 and the second surface 42, the blades will be described in the first to fourth embodiments. The effect can be obtained.
  • Embodiment 6 FIG.
  • an example of an air conditioner including the multi-blade blower 100 described in any of the first to fifth embodiments will be described.
  • items not particularly described are the same as those in any of the first to fifth embodiments, and the same functions and configurations are described using the same reference numerals.
  • FIG. 16 is a refrigerant circuit diagram illustrating an example of an air conditioner according to Embodiment 6 of the present invention.
  • the air conditioner 200 includes a compressor 210, a four-way valve 220, an outdoor heat exchanger 230, an expansion valve 240, and an indoor heat exchanger 250.
  • air conditioner 200 includes multi-blade blower 100 described in any of Embodiments 1 to 5 as a blower that supplies air to indoor heat exchanger 250.
  • the air conditioner 200 includes, for example, a propeller-type blower 260 as a blower that supplies air to the outdoor heat exchanger 230.
  • the multi-blade blower 100 described in any of Embodiments 1 to 5 may be used as a blower that supplies air to outdoor heat exchanger 230.
  • the blower that supplies air to the indoor heat exchanger 250 is A blower other than the multi-blade blower 100 may be used. That is, the air conditioner 200 according to Embodiment 6 includes at least one of the blower that supplies air to the outdoor heat exchanger 230 and the blower that supplies air to the indoor heat exchanger 250 according to Embodiments 1 to Equipped with multi-blade blower 100 described in any of Embodiments 5.
  • the compressor 210 compresses and discharges the sucked refrigerant.
  • the four-way valve 220 is a valve that switches the flow of the refrigerant depending on, for example, a cooling operation and a heating operation.
  • the outdoor heat exchanger 230 exchanges heat between the refrigerant and the outdoor air supplied by the blower 260.
  • the outdoor heat exchanger 230 functions as an evaporator during the heating operation, and evaporates and vaporizes the refrigerant. Further, the outdoor heat exchanger 230 functions as a condenser during the cooling operation, and condenses and liquefies the refrigerant.
  • the expansion valve 240 is, for example, a throttle device or the like, and decompresses and expands the refrigerant.
  • the indoor heat exchanger 250 exchanges heat between the refrigerant and the air supplied by the multi-blade blower 100.
  • the air after the heat exchange in the indoor heat exchanger 250 is supplied to the space to be air-conditioned.
  • the indoor heat exchanger 250 functions as a condenser during the heating operation, and condenses and liquefies the refrigerant.
  • the indoor heat exchanger 250 heats the air supplied by the multiblade blower 100.
  • the indoor heat exchanger 250 functions as an evaporator during the cooling operation, and evaporates and vaporizes the refrigerant.
  • the indoor heat exchanger 250 cools the air supplied by the multi-blade blower 100.
  • the air-conditioning apparatus 200 according to Embodiment 6 heats or cools the multi-blade blower 100 described in any of Embodiments 1 to 5 and the air supplied by the multi-blade blower 100. And a heat exchanger.
  • the air-conditioning apparatus 200 according to Embodiment 6 includes the multi-blade blower 100 having improved ventilation performance as compared with the related art, so that power efficiency is improved.

Landscapes

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

Abstract

La présente invention concerne une soufflante à aubes multiples dans laquelle chaque aube d'une roue à aubes est munie d'un premier bord et d'un second bord constituant des extrémités dans la direction de l'axe de rotation de la roue à aubes. Le premier bord de chaque aube est relié à une plaque principale de la roue à aubes. Le second bord de chaque aube fait face à un orifice d'admission. De plus, dans la même aube, la distance entre l'axe de rotation et l'extrémité circonférentielle interne augmente progressivement vers le second bord à partir d'une première section intermédiaire située entre le premier bord et le second bord, et l'angle d'entrée augmente progressivement de la première section intermédiaire vers le second bord. En outre, lorsque l'extrémité circonférentielle externe de l'aube est vue depuis une direction radiale perpendiculaire à l'axe de rotation, l'extrémité circonférentielle externe adopte une forme approximativement rectiligne et approximativement parallèle à l'axe de rotation.
PCT/JP2018/025172 2018-07-03 2018-07-03 Soufflante à aubes multiples et dispositif de climatisation WO2020008519A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
PCT/JP2018/025172 WO2020008519A1 (fr) 2018-07-03 2018-07-03 Soufflante à aubes multiples et dispositif de climatisation
JP2020528566A JP6945739B2 (ja) 2018-07-03 2018-07-03 多翼送風機及び空気調和装置
CN201880094504.0A CN112352108B (zh) 2018-07-03 2018-07-03 多叶片送风机以及空调装置

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2018/025172 WO2020008519A1 (fr) 2018-07-03 2018-07-03 Soufflante à aubes multiples et dispositif de climatisation

Publications (1)

Publication Number Publication Date
WO2020008519A1 true WO2020008519A1 (fr) 2020-01-09

Family

ID=69060785

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2018/025172 WO2020008519A1 (fr) 2018-07-03 2018-07-03 Soufflante à aubes multiples et dispositif de climatisation

Country Status (3)

Country Link
JP (1) JP6945739B2 (fr)
CN (1) CN112352108B (fr)
WO (1) WO2020008519A1 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN112780599A (zh) * 2020-12-31 2021-05-11 广东美的厨房电器制造有限公司 离心风机以及烹饪器具
CN113309714A (zh) * 2021-05-31 2021-08-27 广东美的厨房电器制造有限公司 多翼离心风机和家用电器
EP4234944A4 (fr) * 2020-10-22 2023-12-13 Mitsubishi Electric Corporation Soufflante centrifuge et dispositif de climatisation
EP4234945A4 (fr) * 2020-10-22 2023-12-13 Mitsubishi Electric Corporation Soufflante centrifuge et dispositif de climatisation

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5413002A (en) * 1977-06-30 1979-01-31 Kawasaki Heavy Ind Ltd Vane rotor of multi-vane type fan
JPH06299994A (ja) * 1993-04-19 1994-10-25 Matsushita Seiko Co Ltd 多翼ファン
JPH07279892A (ja) * 1994-04-06 1995-10-27 Matsushita Seiko Co Ltd 多翼ファン
US20160153457A1 (en) * 2014-11-27 2016-06-02 Samsung Electronics Co., Ltd. Fan assembly for centrifugal blower and air conditioning apparatus including the same

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2003206891A (ja) * 2002-01-17 2003-07-25 Nippon Densan Corp ファンモータ
WO2013080241A1 (fr) * 2011-11-28 2013-06-06 日立アプライアンス株式会社 Ventilateur à pales multiples et climatiseur équipé de ce ventilateur
US10634168B2 (en) * 2015-10-07 2020-04-28 Mitsubishi Electric Corporation Blower and air-conditioning apparatus including the same
CN105508296A (zh) * 2016-01-28 2016-04-20 珠海格力电器股份有限公司 空调室内机、离心风叶与蜗壳的总成及其离心风叶

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5413002A (en) * 1977-06-30 1979-01-31 Kawasaki Heavy Ind Ltd Vane rotor of multi-vane type fan
JPH06299994A (ja) * 1993-04-19 1994-10-25 Matsushita Seiko Co Ltd 多翼ファン
JPH07279892A (ja) * 1994-04-06 1995-10-27 Matsushita Seiko Co Ltd 多翼ファン
US20160153457A1 (en) * 2014-11-27 2016-06-02 Samsung Electronics Co., Ltd. Fan assembly for centrifugal blower and air conditioning apparatus including the same

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP4234944A4 (fr) * 2020-10-22 2023-12-13 Mitsubishi Electric Corporation Soufflante centrifuge et dispositif de climatisation
EP4234945A4 (fr) * 2020-10-22 2023-12-13 Mitsubishi Electric Corporation Soufflante centrifuge et dispositif de climatisation
CN112780599A (zh) * 2020-12-31 2021-05-11 广东美的厨房电器制造有限公司 离心风机以及烹饪器具
CN113309714A (zh) * 2021-05-31 2021-08-27 广东美的厨房电器制造有限公司 多翼离心风机和家用电器
CN113309714B (zh) * 2021-05-31 2024-02-20 广东美的厨房电器制造有限公司 多翼离心风机和家用电器

Also Published As

Publication number Publication date
CN112352108B (zh) 2022-07-19
JP6945739B2 (ja) 2021-10-06
JPWO2020008519A1 (ja) 2021-01-07
CN112352108A (zh) 2021-02-09

Similar Documents

Publication Publication Date Title
CN107850084B (zh) 离心送风机、空气调节装置及制冷循环装置
CN111279085B (zh) 离心送风机、送风装置、空调装置以及制冷循环装置
JP5369141B2 (ja) 空気調和機
WO2020008519A1 (fr) Soufflante à aubes multiples et dispositif de climatisation
EP3626974B1 (fr) Unité extérieure pour climatiseur
JP6381811B2 (ja) 送風機および空気調和装置
CN106481574B (zh) 离心式风机和包括其的空调机
JP6377172B2 (ja) プロペラファン、プロペラファン装置および空気調和装置用室外機
WO2020129179A1 (fr) Ventilateur de soufflage centrifuge, dispositif de soufflage, climatiseur et dispositif à cycle de réfrigération
CN111247345A (zh) 离心送风机、送风装置、空气调节装置以及制冷循环装置
JP2007205268A (ja) 遠心ファン
WO2023135782A1 (fr) Soufflante centrifuge et unité intérieure
JP6695403B2 (ja) 遠心送風機および空気調和装置
JP6430032B2 (ja) 遠心ファン、空気調和装置および冷凍サイクル装置
WO2024214236A1 (fr) Unité intérieure de climatiseur et climatiseur équipé de celle-ci
CN109891101B (zh) 螺旋桨风扇、室外机和制冷循环装置
JP7466765B2 (ja) 送風機、空気調和装置および冷凍サイクル装置
JP7555474B2 (ja) 送風装置および空気調和装置
WO2024189889A1 (fr) Unité intérieure pour climatiseur et climatiseur pourvu de celle-ci
WO2024214327A1 (fr) Soufflante centrifuge, machine de climatisation et dispositif à cycle de réfrigération
JP6685433B2 (ja) 送風機及び空気調和装置
WO2023223383A1 (fr) Ventilateur à flux transversal, dispositif de soufflage, et dispositif à cycle de réfrigération
TW202409480A (zh) 冷凍循環裝置
CN116507809A (zh) 轴流风扇、送风装置以及制冷循环装置

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 18925408

Country of ref document: EP

Kind code of ref document: A1

ENP Entry into the national phase

Ref document number: 2020528566

Country of ref document: JP

Kind code of ref document: A

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 18925408

Country of ref document: EP

Kind code of ref document: A1