The present disclosure relates to a turbo fan in which blade portions are provided on both sides of a main plate, and to an air-sending device, an air-conditioning device, and a refrigeration cycle device each including the turbo fan.
A double-suction turbo fan in which two turbo fans are provided back to back has been proposed (for example, see Patent Literature 1).
Patent Literature 1: Japanese Unexamined Patent Application Publication No. 2011-202821
In the turbo fan disclosed in Patent Literature 1, blade portions are provided on both sides of a main plate. Further, in the turbo fan disclosed in Patent Literature 1, a single blade on one side and a single blade on other side have the same shape. However, in a case where a chord length on the one side and a chord length on the other side are equal to each other in the turbo fan in which the blade portions are provided on both sides of the main plate, airflows discharged from the blade portions may interfere with one another, which may increase noise.
The present disclosure is made to solve the above-described issues, and to provide a turbo fan, an air-sending device, an air-conditioning device, and a refrigeration cycle device each suppressing interference between airflows discharged from blade portions and reducing noise in a turbo fan in which the blade portions are provided on both sides of a main plate.
A turbo fan according to one embodiment of the present disclosure includes a main plate rotationally driven, and a plurality of blade portions arranged at intervals in a circumferential direction on the main plate. The plurality of blade portions include a plurality of first blade portions arranged on one of plate surfaces of the main plate, and a plurality of second blade portions arranged on another plate surface of the main plate. In a case where, in each of the plurality of first blade portions, a length of a virtual straight line connecting a first inner peripheral end part positioned on a rotary shaft side in a radial direction of the main plate and a first outer peripheral end part positioned on an outer edge side of the main plate is defined as a first chord length, and in each of the plurality of second blade portions, a length of a virtual straight line connecting a second inner peripheral end part positioned on the rotary shaft side in the radial direction of the main plate and a second outer peripheral end part positioned on the outer edge side of the main plate is defined as a second chord length, the first chord length and the second chord length are not equal to each other at positions separated by a same distance from the main plate in the axial direction of the rotary shaft.
In the turbo fan according to the embodiment of the present disclosure, the chord length of each of the first blade portions arranged on the one plate surface of the main plate and the chord length of each of the second blade portions arranged on the other plate surface of the main plate are not equal to each other. Therefore, in the turbo fan, a speed difference occurs between airflows passing through the first blade portions and airflows passing through the second blade portions, and phases of the airflows discharged from the respective blade portions can be shifted from each other. As a result, the turbo fan can suppress interference of the airflows discharged from the blade portions, thereby reducing noise.
Hereinafter, turbo fans 10 to 10J, an air-sending device 130, an air-conditioning device 140, and a refrigeration cycle device 150 according to embodiments of the present disclosure are described with reference to drawings. In the following drawings including
The main plate 20 has a disc shape. As illustrated in
The blade portions 30 rotate together with the main plate 20 when the main plate 20 rotates, and move in a circumferential direction of the main plate 20 to generate airflows directed from a center toward an outer periphery of the main plate 20. The plurality of blade portions 30 are arranged at predetermined intervals in the circumferential direction of the main plate 20. The blade portions 30 extend rearward in a rotation direction R of the main plate 20. The plurality of blade portions 30 are circumferentially arranged around the rotary shaft RS, and base ends of the blade portions 30 are fixed to the main plate 20. The blade portions 30 include first blade portions 31 and second blade portions 32. The first blade portions 31 are arranged on one of plate surfaces of the main plate 20, and the second blade portions 32 are arranged on the other plate surface of the main plate 20. In other words, the plurality of blade portions 30 are provided on both sides of the main plate 20 in the axial direction of the rotary shaft RS, and the first blade portions 31 and the second blade portions 32 are provided back to back with the main plate 20 in between. In
Further, in the cross-section in the direction perpendicular to the rotary shaft RS, blade outer peripheral ends of the second blade portions 32 are referred to as second outer peripheral end parts 34, and blade inner peripheral ends of the second blade portions 32 are referred to as second inner peripheral end parts 36. The second inner peripheral end parts 36 are positioned on the rotary shaft RS side in the radial direction of the main plate 20, and the second outer peripheral end parts 34 are positioned on the outer edge side of the main plate 20. A length of a virtual straight line connecting the second outer peripheral end part 34 and the second inner peripheral end part 36 of each of the second blade portions 32 is defined as a second chord length CL2. In other words, the second chord length CL2 is a length of a straight line connecting a leading edge and a trailing edge of each of the second blade portions 32.
Here, the first chord length CL1 and the second chord length CL2 positioned at the same distance from the main plate 20 in the axial direction of the rotary shaft RS are compared. At this time, it is assumed that the first outer peripheral end parts 33 and the second outer peripheral end parts 34 are positioned at the same distance from the main plate 20 in the axial direction of the rotary shaft RS, and the first inner peripheral end parts 35 and the second inner peripheral end parts 36 are positioned at the same distance from the main plate 20 in the axial direction of the rotary shaft RS. Note that, in a case where each of the blade portions 30 is the three-dimensional blade having the twisted shape, for example, the first chord length CL1 and the second chord length CL2 may be lengths at a position where each of the blade portions 30 and the main plate 20 are connected.
In the blade portions 30, the chord length of each of the first blade portions 31 and the chord length of each of the second blade portions 32 are not equal to each other, and the blade inner peripheral ends of the first blade portions 31 and the blade inner peripheral ends of the second blade portions 32 are different in phase in the circumferential direction around the rotary shaft RS. More specifically, in the blade portions 30, the first chord length CL1 of each of the first blade portions 31 and the second chord length CL2 of each of the second blade portions 32 are not equal to each other at positions separated by the same distance from the main plate 20 in the axial direction of the rotary shaft RS of the main plate 20. Further, the first outer peripheral end parts 33 and the second outer peripheral end parts 34 of the blade portions 30 are disposed at the same positions in the radial direction of the main plate 20 and are disposed at the same positions in the radial direction of the main plate 20. Further, the first inner peripheral end parts 35 and the second inner peripheral end parts 36 of the blade portions 30 are disposed at different positions in the radial direction of the main plate 20 or are disposed at different positions in the circumferential direction of the main plate 20. The first chord length CL1 of each of the first blade portions 31 and the second chord length CL2 of each of the second blade portions 32 are not equal to each other, and the first outer peripheral end parts 33 of the first blade portions 31 and the second outer peripheral end parts 34 of the second blade portions 32 are coincident in phase in the circumferential direction around the rotary shaft RS and are coincident in distance in the radial direction around the rotary shaft RS. In other words, the blade phases of the first blade portions 31 and the blade phases of the second blade portions 32 are shifted only on the inner peripheral side but are coincident on the outer peripheral side.
Referring back to
When the main plate 20 of the turbo fan 10 rotates by rotation of the motor connected to the boss portion 25, the blade portions 30 move in the circumferential direction of the main plate 20. When the main plate 20 rotates, air outside the turbo fan 10 is suctioned into a space surrounded by the main plate 20 and the plurality of blade portions 30 through the air inlets 50a. Further, when the blade portions 30 rotate together with the main plate 20 in the circumferential direction of the main plate 20 in the turbo fan 10, the air suctioned into the space surrounded by the main plate 20 and the plurality of blade portions 30 is sent outward in the radial direction of the main plate 20 through a space between the adjacent blade portions 30.
As described above, in the turbo fan 10, the chord length of each of the first blade portions 31 arranged on the one plate surface of the main plate 20 and the chord length of each of the second blade portions 32 arranged on the other plate surface of the main plate 20 are not equal to each other. Therefore, in the turbo fan 10, a speed difference occurs between the airflows passing through the first blade portions 31 and the airflows passing through the second blade portions 32, and the phases of the airflows discharged from the respective blade portions 30 can be shifted from each other. As a result, the turbo fan 10 can suppress interference of the airflows discharged from the blade portions 30, thereby reducing noise.
Further, the first inner peripheral end parts 35 and the second inner peripheral end parts 36 of the blade portions 30 are disposed at different positions in the radial direction of the main plate 20 or are disposed at different positions in the circumferential direction of the main plate 20. Therefore, in the turbo fan 10, the speed difference occurs between the airflows passing through the first blade portions 31 and the airflows passing through the second blade portions 32, and the phases of the airflows discharged from the respective blade portions 30 can be shifted from each other. As a result, the turbo fan 10 can suppress interference of the airflows discharged from the blade portions 30, thereby reducing noise.
For example, in a case where a plurality of turbo fans are mounted on an air-conditioning apparatus, it is necessary to use motors for the respective turbo fans. The turbo fan 10 has the configuration in which the two types of blade portions 30 are provided back to back with the main plate 20 in between, and enables reduction of the number of motors as compared with a case where two turbo fans each including the blade portions provided only on one of plate surfaces of a main plate are used.
Further, the first outer peripheral end parts 33 and the second outer peripheral end parts 34 of the blade portions 30 are disposed at the same positions in the radial direction of the main plate 20 and are disposed at the same positions in the circumferential direction of the main plate 20. When the first outer peripheral end parts 33 and the second outer peripheral end parts 34 that are outer peripheral ends of the blade portions 30 are aligned in phase, it is possible to simultaneously demold the first blade portions 31 and the second blade portions 32 in demolding. More specifically, when the phases of the blade portions 30 within a range SA of each of the side plates 50 illustrated in
In addition, since the turbo fan 10 includes one plate-shaped main plate 20, the turbo fan 10 can be formed in a minimum shape.
When the main plate 20 rotates, the blade portions 30A rotate together with the main plate 20 and move in the circumferential direction of the main plate 20, thereby generating airflows directed from the center toward the outer periphery of the main plate 20. The plurality of blade portions 30A are arranged at predetermined intervals in the circumferential direction of the main plate 20. The plurality of blade portions 30A are circumferentially arranged around the rotary shaft RS, and base ends of the blade portions 30A are fixed to the main plate 20. The blade portions 30A include first blade portions 31A and second blade portions 32A. The first blade portions 31A are arranged on one of plate surfaces of the main plate 20, and the second blade portions 32A are arranged on the other plate surface of the main plate 20. In other words, the plurality of blade portions 30A are provided on both sides of the main plate 20 in the axial direction of the rotary shaft RS, and the first blade portions 31A and the second blade portions 32A are provided back to back with the main plate 20 in between. In
In the blade portions 30A, the chord length of each of the first blade portions 31A and the chord length of each of the second blade portions 32A are not equal to each other, and the first blade portions 31A and the second blade portions 32A are different in phase in the circumferential direction around the rotary shaft RS. More specifically, in the blade portions 30A, the first chord length CL1 of each of the first blade portions 31A and the second chord length CL2 of each of the second blade portions 32A at positions separated by the same distance from the main plate 20 in the axial direction of the rotary shaft RS of the main plate 20 are not equal to each other. Further, the first outer peripheral end parts 33 and the second outer peripheral end parts 34 of the blade portions 30A are disposed at different positions in the radial direction of the main plate 20 or are disposed at different positions in the circumferential direction of the main plate 20. Furthermore, the first inner peripheral end parts 35 and the second inner peripheral end parts 36 of the blade portions 30A are disposed at different positions in the radial direction of the main plate 20 or are disposed at different positions in the circumferential direction of the main plate 20.
As described above, in the turbo fan 10A, the chord length of each of the first blade portions 31A arranged on the one plate surface of the main plate 20 and the chord length of each of the second blade portions 32A arranged on the other plate surface of the main plate 20 are not equal to each other. Therefore, in the turbo fan 10A, a speed difference occurs between the airflows passing through the first blade portions 31A and the airflows passing through the second blade portions 32A, and the phases of the airflows discharged from the respective blade portions 30A can be shifted from each other. As a result, the turbo fan 10A can suppress interference of the airflows discharged from the blade portions 30A, thereby reducing noise.
Further, the first outer peripheral end parts 33 and the second outer peripheral end parts 34 of the blade portions 30A are disposed at different positions in the radial direction of the main plate 20 or are disposed at different positions in the circumferential direction of the main plate 20. In addition, the first inner peripheral end parts 35 and the second inner peripheral end parts 36 of the blade portions 30A are disposed at different positions in the radial direction of the main plate 20 or are disposed at different positions in the circumferential direction of the main plate 20. Therefore, in the turbo fan 10A, the phases of the airflows passing through the first blade portions 31A and the phases of the airflows passing through the second blade portions 32A can be shifted from each other. As a result, the turbo fan 10A can suppress interference of the airflows discharged from the blade portions 30A, thereby reducing noise.
When the main plate 20 rotates, the blade portions 30B rotate together with the main plate 20 and move in the circumferential direction of the main plate 20, thereby generating airflows directed from the center toward the outer periphery of the main plate 20. The plurality of blade portions 30B are arranged at predetermined intervals in the circumferential direction of the main plate 20. The plurality of blade portions 30B are circumferentially arranged around the rotary shaft RS, and base ends of the blade portions 30B are fixed to the main plate 20. The blade portions 30B include first blade portions 31B and second blade portions 32B. The first blade portions 31B are arranged on one of plate surfaces of the main plate 20, and the second blade portions 32B are arranged on the other plate surface of the main plate 20. In other words, the plurality of blade portions 30B are provided on both sides of the main plate 20 in the axial direction of the rotary shaft RS, and the first blade portions 31B and the second blade portions 32B are provided back to back with the main plate 20 in between. It is sufficient for the first blade portions 31B and the second blade portions 32B to be provided back to back with the main plate 20 in between. Therefore, among the blade portions 30B, the first blade portions 31B may be arranged on the upper part of the main plate 20 and the second blade portions 32B may be arranged on the lower part of the main plate 20, or the first blade portions 31B may be arranged on the lower part of the main plate 20 and the second blade portions 32B may be arranged on the upper part of the main plate 20. Each of the blade portions 30B may be formed such that the same cross-sectional shape of the blade continues in the axial direction of the rotary shaft RS, or may be a three-dimensional blade having a twisted shape.
In the blade portions 30B, the chord length of each of the first blade portions 31B and the chord length of each of the second blade portions 32B are not equal to each other, and the first blade portions 31B and the second blade portions 32B are different in phase in the circumferential direction around the rotary shaft RS. More specifically, in the blade portions 30B, the first chord length CL1 of each of the first blade portions 31B and the second chord length CL2 of each of the second blade portions 32B at positions separated by the same distance from the main plate 20 in the axial direction of the rotary shaft RS of the main plate 20 are not equal to each other. Further, the first outer peripheral end parts 33 and the second outer peripheral end parts 34 of the blade portions 30B are disposed at different positions in the radial direction of the main plate 20 or are disposed at different positions in the circumferential direction of the main plate 20. Further, the first inner peripheral end parts 35 and the second inner peripheral end parts 36 of the blade portions 30B are disposed at the same position in the radial direction of the main plate 20 and are disposed at the same position in the circumferential direction of the main plate 20.
As described above, in the turbo fan 10B, the chord length of each of the first blade portions 31B arranged on the one plate surface of the main plate 20 and the chord length of each of the second blade portions 32B arranged on the other plate surface of the main plate 20 are not equal to each other. Therefore, in the turbo fan 10B, a speed difference occurs between the airflows passing through the first blade portions 31B and the airflows passing through the second blade portions 32B, and the phases of the airflows discharged from the respective blade portions 30B can be shifted from each other. As a result, the turbo fan 10B can suppress interference of the airflows discharged from the blade portions 30B, thereby reducing noise.
Further, the first outer peripheral end parts 33 and the second outer peripheral end parts 34 of the blade portions 30B are disposed at different positions in the radial direction of the main plate 20, or are disposed at different positions in the circumferential direction of the main plate 20. Therefore, in the turbo fan 10B the phases of the airflows passing through the first blade portions 31B and the phases of the airflows passing through the second blade portions 32B can be shifted from each other. As a result, the turbo fan 10B can suppress interference of the airflows discharged from the blade portions 30B, thereby reducing noise.
When the main plate 20 rotates, the blade portions 30C rotate together with the main plate 20 and move in the circumferential direction of the main plate 20, thereby generating airflows directed from the center toward the outer periphery of the main plate 20. The plurality of blade portions 30C are arranged at predetermined intervals in the circumferential direction of the main plate 20. The plurality of blade portions 30C are circumferentially arranged around the rotary shaft RS, and base ends of the blade portions 30C are fixed to the main plate 20. The blade portions 30C include first blade portions 31C and second blade portions 32C. The first blade portions 31C are arranged on one of plate surfaces of the main plate 20, and the second blade portions 32C are arranged on the other plate surface of the main plate 20. In other words, the plurality of blade portions 30C are provided on both sides of the main plate 20 in the axial direction of the rotary shaft RS, and the first blade portions 31C and the second blade portions 32C are provided back to back with the main plate 20 in between. In
In the blade portions 30C, the chord length of each of the first blade portions 31C and the chord length of each of the second blade portions 32C are not equal to each other, and the first blade portions 31C and the second blade portions 32C are different in phase in the circumferential direction around the rotary shaft RS. More specifically, in the blade portions 30C, the first chord length CL2 of each of the first blade portions 31C and the second chord length CL2 of each of the second blade portions 32C at positions separated by the same distance from the main plate 20 in the axial direction of the rotary shaft RS of the main plate 20 are not equal to each other. Further, the first outer peripheral end parts 33 and the second outer peripheral end parts 34 of the blade portions 30C are disposed at the same position in the radial direction of the main plate 20 and are disposed at different positions in the circumferential direction of the main plate 20. Further, the first inner peripheral end parts 35 and the second inner peripheral end parts 36 of the blade portions 30C are disposed at different positions in the radial direction of the main plate 20 or are disposed at different positions in the circumferential direction of the main plate 20. The first chord length CL1 of each of the first blade portions 31C and the second chord length CL2 of each of the second blade portions 32C are not equal to each other, and the first outer peripheral end parts 33 of the first blade portions 31 and the second outer peripheral end parts 34 of the second blade portions 32 are different in phase in the circumferential direction around the rotary shaft RS and are coincident in distance in the radial direction around the rotary shaft RS.
The phase shift between the first blade portions 31C and the second blade portions 32C is described in more detail with reference to
As described above, in the turbo fan 10C, the chord length of each of the first blade portions 31C arranged on the one plate surface of the main plate 20 and the chord length of each of the second blade portions 32C arranged on the other plate surface of the main plate 20 are not equal to each other. Therefore, in the turbo fan 10C, a speed difference occurs between the airflows passing through the first blade portions 31C and the airflows passing through the second blade portions 32C, and the phases of the airflows discharged from the respective blade portions 30C can be shifted from each other. As a result, the turbo fan 10C can suppress interference of the airflows discharged from the blade portions 30C, thereby reducing noise.
Further, the first inner peripheral end parts 35 and the second inner peripheral end parts 36 of the blade portions 30C are disposed at different positions in the radial direction of the main plate 20, or are disposed at different positions in the circumferential direction of the main plate 20. Therefore, in the turbo fan 10C, the speed difference occurs between the airflows passing through the first blade portions 31C and the airflows passing through the second blade portions 32C, and the phases of the airflows discharged from the respective blade portions 30C can be shifted from each other. As a result, the turbo fan 10C can suppress interference of the airflows discharged from the blade portions 30C, thereby reducing noise.
Further, the first outer peripheral end parts 33 and the second outer peripheral end parts 34 of the blade portions 30C are disposed at the same position in the radial direction of the main plate 20, and are disposed at different positions in the circumferential direction of the main plate 20. Therefore, in the turbo fan 10C, the phases of the airflows discharged from the first blade portions 31C and the phases of the airflows discharged from the second blade portions 32C can be shifted from each other. As a result, the turbo fan 10C can suppress interference of the airflows discharged from the blade portions 30C, thereby reducing noise.
Further, the first inner peripheral end parts 35 and the second inner peripheral end parts 36 of the blade portions 30C are disposed at different positions in the radial direction of the main plate 20, or are disposed at different positions in the circumferential direction of the main plate 20. In addition, the first outer peripheral end parts 33 and the second outer peripheral end parts 34 of the blade portions 30C are disposed at the same position in the radial direction of the main plate 20, and are disposed at different positions in the circumferential direction of the main plate 20. Since the phases of the first blade portions 31C and the phases of the second blade portions 32C of the blade portions 30C are shifted from each other through the main plate 20, the speed difference occurs between the airflows passing through the first blade portions 31C and the airflows passing through the second blade portions 32C, which makes it possible to shift the phases of the airflows discharged from the respective blade portions 30C. As a result, the turbo fan 10C can suppress interference of the airflows discharged from the blade portions 30C, thereby reducing noise.
Moreover, the blade portions 30C are provided such that the relationship of angle θ2≤(angle θ1)/2 is established. Since the advancing angle between each of the first blade portions 31C and the corresponding second blade portion 32C is small in the turbo fan 10C, the first blade portions 31C and the second blade portions 32C can be easily demolded at the same time. Accordingly, the turbo fan 10C enables reduction in molding cost in manufacturing of the turbo fan 10C.
When the main plate 20 rotates, the blade portions 30D rotate together with the main plate 20 and move in the circumferential direction of the main plate 20, thereby generating airflows directed from the center toward the outer periphery of the main plate 20. The plurality of blade portions 30D are arranged at predetermined intervals in the circumferential direction of the main plate 20.The plurality of blade portions 30D are circumferentially arranged around the rotary shaft RS, and base ends of the blade portions 30D are fixed to the main plate 20. The blade portions 30D include first blade portions 31D and second blade portions 32D. The first blade portions 31D are arranged on one of plate surfaces of the main plate 20, and the second blade portions 32D are arranged on the other plate surface of the main plate 20. In other words, the plurality of blade portions 30D are provided on both sides of the main plate 20 in the axial direction of the rotary shaft RS, and the first blade portions 31Dand the second blade portions 32D are provided back to back with the main plate 20 in between. In
the cross-section in the direction perpendicular to the rotary shaft RS, blade outer peripheral ends of the first blade portions 310 are referred to as the first outer peripheral end parts 33, and blade inner peripheral ends of the first blade portions 31D are referred to as the first inner peripheral end parts 35. In addition, a length of a straight line connecting the first outer peripheral end part 33 and the first inner peripheral end part 35 of each of the first blade portions 31Dis defined as the first chord length CL1. Further, in the cross-section in the direction perpendicular to the rotary shaft RS, blade outer peripheral ends of the second blade portions 32D are referred to as the second outer peripheral end parts 34, and blade inner peripheral ends of the second blade portions 32D are referred to as the second inner peripheral end parts 36. In addition, a length of a straight line connecting the second outer peripheral end part 34 and the second inner peripheral end part 36 of each of the second blade portions 32D is defined as the second chord length CL2. Here, the first chord length CL1 and the second chord length CL2 positioned at the same distance from the main plate 20 in the axial direction of the rotary shaft RS are compared. At this time, it is assumed that the first outer peripheral end parts 33 and the second outer peripheral end parts 34 are positioned at the same distance from the main plate 20 in the axial direction of the rotary shaft RS, and the first inner peripheral end parts 35 and the second inner peripheral end parts 36 are positioned at the same distance from the main plate 20 in the axial direction of the rotary shaft RS. Note that, in the case where each of the blade portions 30D is the three-dimensional blade having the twisted shape, for example, the first chord length CL1 and the second chord length CL2 may be lengths at a position where each of the blade portions 30D and the main plate 20 are connected,
In the blade portions 30D, the chord length of each of the first blade portions 31D and the chord length of each of the second blade portions 32D are not equal to each other, and the first blade portions 31D and the second blade portions 32D are different in phase in the circumferential direction around the rotary shaft RS. More specifically, in the blade portions 30D, the first chord length CL1 of each of the first blade portions 31D and the second chord length CL2 of each of the second blade portion 32D are not equal to each other. Further, the first outer peripheral end parts 33 and the second outer peripheral end parts 34 of the blade portions 30D are disposed at the same position in the radial direction of the main plate 20 and are disposed at different positions in the circumferential direction of the main plate 20. Furthermore, the first inner peripheral end parts 35 and the second inner peripheral end parts 36 of the blade portions 30D are not disposed at the same position in at least one of the radial direction and the circumferential direction of the main plate 20, The first chord length CL1 of each of the first blade portions 31D and the second chord length CL2 of each of the second blade portions 32D are not equal to each other, and the first outer peripheral end parts 33 of the first blade portions 31D and the second outer peripheral end parts 34 of the second blade portions 32D are different in phase in the circumferential direction around the rotary shaft RS and are coincident in distance in the radial direction around the rotary shaft RS.
The phase shift between the first blade portions 31D and the second blade portions 32D is described in more detail with reference to
As described above, in the turbo fan 10D, the chord length of each of the first blade portions 31D arranged on the one plate surface of the main plate 20 and the chord length of each of the second blade portions 32D arranged on the other plate surface of the main plate 20 are not equal to each other. Therefore, in the turbo fan 10D, a speed difference occurs between the airflows passing through the first blade portions 31D and the airflows passing through the second blade portions 320, and the phases of the airflows discharged from the respective blade portions 30D can be shifted from each other. As a result, the turbo fan 10D can suppress interference of the airflows discharged from the blade portions 30D, thereby reducing noise.
Further, the first inner peripheral end parts 35 and the second inner peripheral end parts 36 of the blade portions 30D are disposed at different positions in the radial direction of the main plate 20, or are disposed at different positions in the circumferential direction of the main plate 20. Therefore, in the turbo fan 10D, the speed difference occurs between the airflows passing through the first blade portions 31D and the airflows passing through the second blade portions 32D, and the phases of the airflows discharged from the respective blade portions 30D can be shifted from each other. As a result, the turbo fan 10D can suppress interference of the airflows discharged from the blade portions 30D, thereby reducing noise.
Further, the first outer peripheral end parts 33 and the second outer peripheral end parts 34 of the blade portions 30D are disposed at the same position in the radial direction of the main plate 20, and are disposed at different positions in the circumferential direction of the main plate 20. Therefore, in the turbo fan 10D, the phases of the airflows discharged from the first blade portions 31D and the phases of the airflows discharged from the second blade portions 32D can be shifted from each other. As a result, the turbo fan 10D can suppress interference of the airflows discharged from the blade portions 30D, thereby reducing noise.
Further, the first inner peripheral end parts 35 and the second inner peripheral end parts 36 of the blade portions 30D are disposed at different positions in the radial direction of the main plate 20, or are disposed at different positions in the circumferential direction of the main plate 20. In addition, the first outer peripheral end parts 33 and the second outer peripheral end parts 34 of the blade portions 30D are disposed at the same position in the radial direction of the main plate 20, and are disposed at different positions in the circumferential direction of the main plate 20.
Since the phases of the first blade portions 31D and the phases of the second blade portions 32D of the blade portions 30D are shifted from each other through the main plate 20, the speed difference occurs between the airflows passing through the first blade portions 31D and the airflows passing through the second blade portions 32D, which makes it possible to shift the phases of the airflows discharged from the respective blade portions 30D. As a result, the turbo fan 10D can suppress interference of the airflows discharged from the blade portions 30D, thereby reducing noise.
Moreover, when the rotary shaft RS is viewed in the axial direction, the blade portions 30D are provided such that the first blade portion 31C and the fourth blade portion 32D1 intersect with each other with the main plate 20 in between. Therefore, in the turbo fan 10D, the speed difference occurs between the airflows passing through the first blade portions 31D and the airflows passing through the second blade portions 32D, and the phases of the airflows discharged from the respective blade portions 30D can be shifted from each other. As a result, the turbo fan 10D can suppress interference of the airflows discharged from the blade portions 30D, thereby reducing noise.
Moreover, the blade portions 30D are provided such that the relationship of angle θ4≤±(angle θ3)/2 is established. Since the advancing angle between each of the first blade portions 31D and the corresponding second blade portion 32D is small in the turbo fan 10D, the first blade portions 31D and the second blade portions 32D can be easily demolded at the same time. Accordingly, the turbo fan 10D enables reduction in molding cost in manufacturing of the turbo fan 10D.
As illustrated in
As described above, since the blade portions 30E have the relationship of second blade outer diameter D>first blade outer diameter C, it is possible to uniformize a blowout wind velocity of the air in the axial direction of the rotary shaft RS.
Further, since the blade portions 30E have the relationship of second blade inner diameter F>first blade inner diameter E, each of the blade portions 30E has the inclined part 30E4 from the front end part 30E1 to the base part 30E2 on the inner periphery thereof in the axial direction of the rotary shaft RS. In addition, each of the blade portions 30E has the relationship of blade inlet angle θ≤90 degrees. With the above-described configurations, the blade portions 30E can reduce separation of the airflows from the blades when the air is suctioned, thereby reducing noise.
A blade outlet angle at the base part 30E2 of each of the blade portions 30F is defined as the blade outlet angle Φ1. In addition, a blade outlet angle at the front end part 30E1 of each of the blade portions 30F is defined as the blade outlet angle Φ2. In the turbo fan 10F, each of the blade portions 30F has relationship of blade outlet angle Φ1≥blade outlet angle Φ2.
As described above, since each of the blade portions 30F of the turbo fan 10F has the relationship of blade outlet angle Φ1≥blade outlet angle Φ2, it is possible to increase the wind velocity on the main plate side on which the outer peripheral diameter is small, to increase PQ characteristics, and to suppress ventilation resistance. This makes it possible to improve efficiency.
The casing 90 houses the main plate 20 and the blade portions 30, and includes the air inlets 92c from which the air to be suctioned into the blade portions 30 is taken in and an air outlet 91a from which the air sent by the blade portions 30 is discharged. The casing 90 surrounds the blade portions 30, and straightens the air blown out from the blade portions 30. The casing 90 includes a discharge portion 91 and a scrod portion 92. The discharge portion 91 forms the air outlet 91a from which the airflows generated by the blade portions 30 and passing through the scroll portion 92 is discharged. The scroll portion 92 forms an air passage that converts dynamic pressure of the airflows generated by the blade portions 30 into static pressure. The scroll portion 92 includes the side walls 92a that cover the blade portions 30 from the axial direction of the rotary shaft RS of the turbo fan 10 and each have the air inlet 92c from which the air is taken in, and a peripheral wall 92b that surrounds the blade portions 30 from the radial direction of the rotary shaft RS. The scroll portion 92 further includes a tongue portion 93 that guides the airflows generated by the blade portions 30 to the air outlet 91a through the scroll portion 92. The radial direction of the rotary shaft RS is a direction perpendicular to the rotary shaft RS. An internal space of the scroll portion 92 configured by the peripheral wall 92b and the side walls 92a is a space through which the air blown out from the blade portions 30 flows along the peripheral wall 92b.
In the turbo fan 10G, the casing 90 has the two side walls 92a that are disposed to face each other. The side walls 92a are disposed perpendicularly to the axial direction of the rotary shaft RS of the blade portions 30, to cover at least a part of the blade portions 30. The side walls 92a of the casing 90 each have the air inlet 92c that enables the air to flow between the blade portions 30 and an outside of the casing 90. Further, the side walls 92a each include a bell mouth 94 that guides the airflow suctioned into the casing 90 through the air inlet 92c. The bell mouths 94 are provided at positions facing the air inlets 30E3 of the blade portions 30. Each of the bell mouths 94 has a cylindrical shape, and is formed such that the air passage is narrowed from an upstream side to a downstream side of the airflow suctioned into the casing 90 through the air inlet 92c. The air inlets 92c each have a circular shape, and are formed such that centers of the respective air inlets 92c are coincident with the center of the rotary shaft RS of the blade portions 30. The configurations of the side walls 92a cause the air near the air inlets 92c to smoothly flow and to efficiently flow into the blade portions 30 from the air inlets 92c.
The peripheral wall 92b surrounds the blade portions 30 from the radial direction of the rotary shaft RS, and has an inner peripheral surface opposite to the outer peripheral side of the blade portions 30 in the radial direction. As illustrated in
The discharge portion 91 is made of a hollow pipe that has a rectangular cross-section orthogonal to the flow direction of the air flowing along the peripheral wall 92b. The discharge portion 91 forms a flow path that guides and discharges the air sent from the blade portions 30 and flowing in the gap between the peripheral wall 92b and the blade portions 30, to the outside. The discharge portion 91 forms the air outlet 91a from which the air flowing through the flow path inside the discharge portion 91 is discharged to the outside.
As illustrated in
When the blade portions 30 rotate together with the main plate 20, air outside the casing 90 is suctioned into the casing 90 through the air inlets 92c. The air suctioned into the casing 90 is guided by the bell mouths 94 and suctioned into the blade portions 30. The air suctioned into the blade portions 30 becomes airflows with dynamic pressure and static pressure in the course of passing through spaces among the plurality of blade portions 30, and the airflows are then blown out outward in the radial direction of the blade portions 30. The dynamic pressure of the airflows blown out from the blade portions 30 is converted into the static pressure while the airflows are guided between the inside of the peripheral wall 92b and the blade portions 30 of the scroll portion 92. Thereafter, the airflows blown out from the blade portions 30 pass through the scroll portion 92, and are then blown out to the outside of the casing 90 from the air outlet 91a provided at the discharge portion 91.
As described above, since the turbo fan 10G includes the casing 90 or the casing 90A, it is possible to convert the dynamic pressure of the airflows generated by the blade portions 30 into the static pressure. Further, since the turbo fan 10G includes the casing 90 or the casing 90A, it is possible to specify the blowout direction of the air.
The discharge portion 91 of the casing 90 includes the fins 97 extending between the first side plate 91d and the second side plate 91e. The fins 97 are provided between wall portions configuring the air outlet 91a. The fins 97 are plate-shaped parts. The fins 97 are provided in parallel with the rotary shaft RS. One fin 97 may be provided or a plurality of fins 97 may be provided. In a case where the plurality of fins 97 are provided, the plurality of fins 97 are arranged side by side and in parallel with one another between the extension plate 91b and the diffuser plate 91c.
As described above, the turbo fan 10H includes the fins 97 extending between the first side plate 91d and the second side plate 91e in the discharge portion 91 of the casing 90. Therefore, for example, in a case where the turbo fan 10H is installed inside an indoor unit of an air-conditioning device, the flowing direction of the airflows discharged from the turbo fan 10H can be directed to a heat exchanger, which makes it possible to improve efficiency of heat exchange. The turbo fan 10I includes the fins 97 and the fins 98 provided in the lattice shape in the discharge portion 91 of the casing 90. Therefore, the flowing direction of the airflows discharged from the turbo fan 10I can be further specified, which makes it possible to further improve efficiency of a unit in which the turbo fan 10I is installed.
[Action and Effects of Turbo Fan 10J]As described above, since the main plate 20 of the turbo fan 10J includes the first plate portion 21 and the second plate portion 22, the turbo fan 10J can be configured by combining two existing turbo fans each including the blade portions 30 on one of surfaces of the main plate 20. Further, although the main plate 20 of the turbo fan 10J includes the first plate portion 21 and the second plate portion 22, the turbo fan 10J can be realized by a small configuration by providing the motor on the outside of the casing 90. In addition, in the turbo fan 10J, the first plate portion 21 and the second plate portion 22 are disposed in parallel with each other, and the boss portion 25 is provided at the center parts of the first plate portion 21 and the second plate portion 22 to couple the first plate portion 21 and the second plate portion 22. Therefore, it is sufficient to provide one motor coupled with the boss portion 25, which makes it possible to reduce the number of used motors as compared with a case where motors are coupled with the respective existing turbo fans each including the blade portions 30 on one of surfaces of the main plate 20.
When the blade portions 30 rotate by driving of a motor 6 in the air-sending device 130, air is suctioned into the case 7 through the air inlet 71. The air suctioned into the case 7 is guided by the bell mouths 94, and is suctioned into the blade portions 30. The air suctioned into the blade portions 30 is blown out outward in the radial direction of the blade portions 30. The air blown out from the blade portions 30 passes through the inside of the casing 90, is then blown out from the air outlet 91a of the casing 90, and is blown out from the air outlet 72 of the case 7.
Since the air-sending device 130 according to Embodiment 11 includes any one of the turbo fans 10 to 10J according to Embodiments 1 to 10, the air-sending device 130 can realize noise reduction.
As illustrated in
The two turbo fans 10G, the fan motor 9, and the heat exchanger 15 are housed inside the case 16. Each of the turbo fans 10G includes the blade portions 30 and the casing 90 provided with the bell mouths 94. The fan motor 9 is supported by a motor support 9a fixed to the upper surface portion 16a of the case 16. The fan motor 9 has an output shaft 6a. The output shaft 6a is disposed to extend in parallel with the surface provided with the case air inlet 18 and the surface provided with the case air outlet 17 among the side surface portions 16c. As illustrated in
As illustrated in
As illustrated in
When the blade portions 30 rotate together with the main plates 20, the air in the air-conditioned space is suctioned into the case 16 through the case air inlet 18 or the case air inlet 18a. The air suctioned into the case 16 is guided by the bell mouths 94 and is suctioned into the blade portions 30. The air suctioned into the blade portions 30 is blown out outward in the radial direction of the blade portions 30. The air blown out from the blade portions 30 passes through the inside of the casing 90, is then blown out from the air outlets 91a of the casings 90, and is supplied to the heat exchanger 15. At this time, when the casing 90 has the fins 97, or the fins 97 and the fins 98, the airflows are easily guided from the turbo fans 10G to the heat exchanger 15. The air supplied to the heat exchanger 15 is subjected to heat exchange when passing through the heat exchanger 15, and is adjusted in temperature and humidity. The air passing through the heat exchanger 15 is blown out from the case air outlet 17 to the air-conditioned space.
Since the air-conditioning device 140 according to Embodiment 12 includes any one of the turbo fans 10 to 10J according to Embodiments 1 to 10, the air-conditioning device 140 can realize noise reduction.
The refrigeration cycle device 150 according to Embodiment 13 performs air conditioning by moving heat between outside air and indoor air through refrigerant to heat or cool an inside of a room. The refrigeration cycle device 150 according to Embodiment 13 includes an outdoor unit 100 and an indoor unit 200. In the refrigeration cycle device 150, the outdoor unit 100 and the indoor unit 200 are connected by a refrigerant pipe 300 and a refrigerant pipe 400 to configure a refrigerant circuit through which the refrigerant circulates. The refrigerant pipe 300 is a gas pipe through which gas-phase refrigerant flows, and the refrigerant pipe 400 is a liquid pipe through which liquid-phase refrigerant flows. Note that two-phase gas-liquid refrigerant may flow through the refrigerant pipe 400. In the refrigerant circuit of the refrigeration cycle device 150, a compressor 101, a flow switching device 102, an outdoor heat exchanger 103, an expansion valve 105, and an indoor heat exchanger 201 are sequentially connected through the refrigerant pipes.
The outdoor unit 100 includes the compressor 101, the flow switching device 102, the outdoor heat exchanger 103, and the expansion valve 105. The compressor 101 compresses suctioned refrigerant and discharges the compressed refrigerant. The compressor 101 may include an inverter device, and may have a configuration in which an operation frequency is changed by the inverter device to change a capacity of the compressor 101. The capacity of the compressor 101 is an amount of the refrigerant sent per unit time. The flow switching device 102 is, for example, a four-way valve, and switches a direction of a refrigerant flow path. The refrigeration cycle device 150 can realize heating operation or cooling operation by causing the flow switching device 102 to switch the flow of the refrigerant based on an instruction from a controller (not illustrated).
The outdoor heat exchanger 103 exchanges heat between the refrigerant and outdoor air. During the heating operation, the outdoor heat exchanger 103 functions as an evaporator, and exchanges heat between low-pressure refrigerant flowing from the refrigerant pipe 400 and the outdoor air, thereby evaporating and gasifying the refrigerant. During the cooling operation, the outdoor heat exchanger 103 functions as a condenser, and exchanges heat between the refrigerant compressed by the compressor 101 and flowing from the flow switching device 102 and the outdoor air, thereby condensing and liquefying the refrigerant. To enhance efficiency of the heat exchange between the refrigerant and the outdoor air, the outdoor heat exchanger 103 includes an outdoor air-sending device 104. The outdoor air-sending device 104 may include an inverter device, and an operation frequency of a fan motor may be changed to change a rotation speed of a fan. The expansion valve 105 is an expansion device (flow rate control unit). The expansion valve 105 functions as an expansion valve by adjusting a flow rate of the refrigerant flowing through the expansion valve 105, and changes an opening degree to adjust pressure of the refrigerant. For example, in a case where the expansion valve 105 is an electronic expansion valve, the opening degree is adjusted based on an instruction of the controller (not illustrated).
The indoor unit 200 includes the indoor heat exchanger 201 exchanging heat between the refrigerant and the indoor air, and an indoor air-sending device 202 that adjusts flow of the air, the heat of which is exchanged by the indoor heat exchanger 201. During the heating operation, the indoor heat exchanger 201 functions as a condenser, and exchanges heat between the refrigerant flowing from the refrigerant pipe 300 and the indoor air to condense and liquefy the refrigerant, and causes the refrigerant to flow out to the refrigerant pipe 400. During the cooling operation, the indoor heat exchanger 201 functions as an evaporator, and exchanges heat between the refrigerant put into a low-pressure state by the expansion valve 105 and the indoor air, causes the refrigerant to remove the heat of the air to evaporate and gasify the refrigerant, and causes the refrigerant to flow out to the refrigerant pipe 300. The indoor air-sending device 202 is provided to face the indoor heat exchanger 201. One or more of the turbo fans 10 to 10J according to Embodiments 1 to 10 are applied for the indoor air-sending device 202. An operation speed of the indoor air-sending device 202 is determined by user setting. The indoor air-sending device 202 may include an inverter device, and an operation frequency of a fan motor (not illustrated) may be changed to change the rotation speed of the main plate 20.
Next, the cooling operation is described as an operation example of the refrigeration cycle device 150. The high-temperature high-pressure gas refrigerant compressed and discharged by the compressor 101 flows into the outdoor heat exchanger 103 through the flow switching device 102. The gas refrigerant flowing into the outdoor heat exchanger 103 is condensed by heat exchange with the outside air sent by the outdoor air-sending device 104, into low-temperature refrigerant, and the low-temperature refrigerant flows out from the outdoor heat exchanger 103. The refrigerant flowing out from the outdoor heat exchanger 103 is expanded and decompressed by the expansion valve 105, into low-temperature low-pressure two-phase gas-liquid refrigerant. The two-phase gas-liquid refrigerant flows into the indoor heat exchanger 201 of the indoor unit 200 and evaporates by heat exchange with the indoor air sent by the indoor air-sending device 202, into low-temperature low-pressure gas refrigerant, and the low-temperature low-pressure gas refrigerant flows out from the indoor heat exchanger 201. At this time, the indoor air cooled through heat removal by the refrigerant is blown out as air-conditioning air from an air outlet of the indoor unit 200 to the air-conditioned space. The gas refrigerant flowing out from the indoor heat exchanger 201 is suctioned into the compressor 101 through the flow switching device 102, and is compressed again. The above-described operation is repeated.
Next, the heating operation is described as an operation example of the refrigeration cycle device 150. The high-temperature high-pressure gas refrigerant compressed and discharged by the compressor 101 flows into the indoor heat exchanger 201 of the indoor unit 200 through the flow switching device 102. The gas refrigerant flowing into the indoor heat exchanger 201 is condensed by heat exchange with the indoor air sent by the indoor air-sending device 202, into low-temperature refrigerant, and the low-temperature refrigerant flows out from the indoor heat exchanger 201. At this time, the indoor air warmed by receiving heat from the gas refrigerant is blown out as the air-conditioning air from the air outlet of the indoor unit 200 to the air-conditioned space. The refrigerant flowing out from the indoor heat exchanger 201 is expanded and decompressed by the expansion valve 105, into low-temperature low-pressure two-phase gas-liquid refrigerant. The two-phase gas-liquid refrigerant flows into the outdoor heat exchanger 103 of the outdoor unit 100, evaporates by heat exchange with the outside air sent by the outdoor air-sending device 104 into low-temperature low-pressure gas refrigerant, and the low-temperature low-pressure gas refrigerant flows out from the outdoor heat exchanger 103. The gas refrigerant flowing out from the outdoor heat exchanger 103 is suctioned into the compressor 101 through the flow switching device 102, and is compressed again. The above-described operation is repeated.
Since the refrigeration cycle device 150 according to Embodiment 13 includes one or more of the turbo fans 10 to 10J according to Embodiments 1 to 10, the refrigeration cycle device 150 can realize noise reduction.
The configurations described in the above-described embodiments illustrate examples of the contents of the present disclosure. The configurations can be combined with other well-known techniques, and a part of the configurations can be omitted and modified without departing from the scope of the present disclosure.
6: motor, 6a: output shaft, 7: case, 9: fan motor, 9a: motor support, 10: turbo fan, 10A: turbo fan, 10B: turbo fan, 10C: turbo fan, 10D: turbo fan, 10E: turbo fan, 10F: turbo fan, 10G: turbo fan, 10H: turbo fan, 10I: turbo fan, 10J: turbo fan, 15: heat exchanger, 16: case, 16a: upper surface portion, 16b: lower surface portion, 16c: side surface portion, 17: case air outlet, 18: case air inlet, 18a: case air inlet, 19: partition, 20: main plate, 21: first plate portion, 22: second plate portion, 25: boss portion, 30: blade portion, 30A: blade portion, 30B: blade portion, 30C: blade portion, 30D: blade portion, 30E: blade portion, 30E1: front end part, 30E2: base part, 30E3: air inlet, 30E4: inclined part, 30F: blade portion, 31: first blade portion, 31A: first blade portion, 31B: first blade portion, 31C: first blade portion, 31C1: first reference blade portion, 31C2: third blade portion, 31D: first blade portion, 31D1: first reference blade portion, 31D2: third blade portion, 32: second blade portion, 32A: second blade portion, 32B: second blade portion, 32C: second blade portion, 3201: fourth blade portion, 32D: second blade portion, 32D1: fourth blade portion, 33: first outer peripheral end part, 33A: third outer peripheral end part, 34: second outer peripheral end part, 34A: fourth outer peripheral end part, 35: first inner peripheral end part, 36: second inner peripheral end part, 50: side plate, 50a: air inlet, 50c: outer peripheral ring, 71: air inlet, 72: air outlet, 73: partition, 90: casing, 90A: casing, 91: discharge portion, 91a: air outlet, 91b: extension plate, 91c: diffuser plate, 91d: first side plate, 91e: second side plate, 92: scroll portion, 92a: side wall, 92b: peripheral wall, 92c: air inlet, 93: tongue portion, 94: bell mouth, 97: fin, 98: fin, 100: outdoor unit, 101: compressor, 102: flow switching device, 103: outdoor heat exchanger, 104: outdoor air-sending device, 105: expansion valve, 130: air-sending device, 140: air-conditioning device, 150: refrigeration cycle device, 200: outdoor unit, 201: indoor heat exchanger, 202: indoor air-sending device, 300: refrigerant pipe, 400: refrigerant pipe
Filing Document | Filing Date | Country | Kind |
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PCT/JP2018/040324 | 10/30/2018 | WO | 00 |