CN113302401B - Blower, indoor unit and air conditioner - Google Patents
Blower, indoor unit and air conditioner Download PDFInfo
- Publication number
- CN113302401B CN113302401B CN201980088500.6A CN201980088500A CN113302401B CN 113302401 B CN113302401 B CN 113302401B CN 201980088500 A CN201980088500 A CN 201980088500A CN 113302401 B CN113302401 B CN 113302401B
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- Prior art keywords
- blower
- side plate
- extending direction
- width
- peripheral end
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/26—Rotors specially for elastic fluids
- F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
- F04D29/281—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for fans or blowers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D25/00—Pumping installations or systems
- F04D25/02—Units comprising pumps and their driving means
- F04D25/06—Units comprising pumps and their driving means the pump being electrically driven
- F04D25/0606—Units comprising pumps and their driving means the pump being electrically driven the electric motor being specially adapted for integration in the pump
Abstract
A blower (100) is provided with a motor (20) that includes a rotation shaft (21) and a drive unit (22), and a centrifugal fan (10) that includes: a main plate (11) fixed to the rotation shaft (21); an annular side plate (13) arranged at a distance from the main plate (11) in the direction of extension of the rotation shaft; and a plurality of blades (12) arranged between the main plate (11) and the side plate (13). The main plate (11) has a convex portion (16), and the convex portion (16) is arranged at the center in the radial direction and is convex toward the side plate (13) side in the extending direction. The convex portion (16) has a convex surface (16 a) and a concave surface (16 b) in which at least a part of the driving portion (22) is accommodated. The height (a) of the protruding part (16) in the extending direction is smaller than half the width (b) of the air outlet (15) in the extending direction. The width (c) of the portion of the driving part (22) which is arranged in the concave part (19) in the extending direction is wider than half of the width (d) of the driving part (22) in the extending direction.
Description
Technical Field
The present invention relates to an air blower, an indoor unit, and an air conditioner.
Background
A blower provided with a centrifugal fan is known. International publication No. 2006/126408 discloses a blower including a main plate and a shroud (side plate) arranged at intervals in an extending direction of a rotary shaft, and a plurality of blades arranged between the main plate and the shroud. The central part of the main plate in the radial direction is provided in a convex shape relative to the outer peripheral part when the centrifugal fan is viewed from the suction inlet. The central portion of the main plate is recessed with respect to the outer peripheral portion when the centrifugal fan is viewed from a side opposite to the suction port. A motor for rotating the blower is accommodated in the concave portion of the central portion. The inner peripheral end of each blade of the centrifugal fan is provided on the convex portion.
Prior art literature
Patent literature
Patent document 1: international publication No. 2006/126408
Disclosure of Invention
Problems to be solved by the invention
However, the convex portion of the main plate prevents the air flow from the suction port of the centrifugal fan to the main plate side in the extending direction between the blades. As a result, the pressure on the main plate side in the extending direction is reduced between the blades, and therefore the airflow is sucked toward the main plate side, and the wind speed distribution in the extending direction between the blades becomes uneven. As a result, a decrease in air blowing efficiency and an increase in noise are caused. The higher the height of the central portion in the extending direction, the more remarkable the problem.
On the other hand, if the height of the central portion of the main plate in the extending direction is reduced, the protruding portion of the motor disposed outside the concave portion of the main plate in the extending direction is enlarged, and the blower is enlarged in the extending direction.
The main object of the present invention is to provide a blower, which is capable of suppressing the reduction of the blower efficiency, the increase of the noise and the enlargement of the blower compared with the conventional blower.
Means for solving the problems
The blower of the present invention is provided with a motor and a centrifugal fan, wherein the motor comprises a rotating shaft and a driving part for rotating the rotating shaft, and the centrifugal fan comprises: a main plate fixed to the rotation shaft; an annular side plate disposed at a distance from the main plate in the extending direction of the rotary shaft; and a plurality of blades arranged between the main plate and the side plate, wherein the centrifugal fan is rotated by a motor. In the centrifugal fan, a blow-out port is provided between the radial outer peripheral end portion of the main plate and the radial outer peripheral end portion of the side plate. The main plate has a convex portion that is disposed at the center in the radial direction and that is convex toward the side plate side in the extending direction. The convex portion has a convex surface provided in a convex shape and a concave surface arranged on the opposite side to the convex surface. At least a part of the driving portion is accommodated in the concave portion surrounded by the concave surface. The height a of the protruding portion in the extending direction is smaller than half the width b of the air outlet in the extending direction. The width c of the portion of the driving portion disposed inside the recess in the extending direction is wider than half of the width d of the driving portion in the extending direction.
Effects of the invention
According to the present invention, it is possible to provide a blower which suppresses a decrease in blower efficiency, an increase in noise, and an increase in size, as compared with conventional blowers.
Drawings
Fig. 1 is a perspective view showing a blower according to embodiment 1.
Fig. 2 is a sectional view of the blower shown in fig. 1 taken along the rotation axis.
Fig. 3 is a graph showing a relationship between the fan input and the ratio a/b of the blower according to embodiment 1.
Fig. 4 is a cross-sectional view of the blower of embodiment 2 taken along the rotation axis.
Fig. 5 is a cross-sectional view of the blower of embodiment 3 taken along the rotation axis.
Fig. 6 is a cross-sectional view of the blower of embodiment 4 taken along the rotation axis.
Fig. 7 is a cross-sectional view of the blower of embodiment 5 taken along the rotation axis.
Fig. 8 is a cross-sectional view of the blower and the indoor unit according to embodiment 6 taken along the rotation axis.
Fig. 9 is a diagram showing an air conditioner provided with a blower according to any one of embodiments 1 to 6.
Detailed Description
Hereinafter, embodiments of the present invention will be described with reference to the drawings. In the following drawings, the same or corresponding parts are denoted by the same reference numerals, and the description thereof will not be repeated.
Embodiment 1
As shown in fig. 1 and 2, the blower 100 according to embodiment 1 includes a centrifugal fan 10 and a motor 20. The centrifugal fan 10 includes a main plate 11, a plurality of blades 12, and a side plate 13. The motor 20 includes a rotation shaft 21, a driving portion 22, and a supporting portion 23. Hereinafter, the extending direction of the rotary shaft 21, the radial direction with respect to the extending direction, and the circumferential direction will be simply referred to as the extending direction, the radial direction, and the circumferential direction.
The centrifugal fan 10 is rotationally symmetrical with respect to the rotation shaft 21 by an arbitrary number of bits. The centrifugal fan 10 is provided with a suction port 14 and a blowout port 15, the suction port 14 being arranged at the center in the radial direction and opening in the extending direction, and the blowout port 15 being arranged at the outer side in the radial direction than the suction port 14 and opening in a direction intersecting the extending direction.
The main plate 11 is fixed to the rotation shaft 21. The side plate 13 is disposed on the opposite side of the motor 20 from the main plate 11 in the extending direction. The main plate 11 has a convex portion 16, and the convex portion 16 is arranged at the center in the radial direction and is convex toward the suction port 14 when the main plate 11 is viewed from the side plate 13 side. The convex portion 16 protrudes toward the side plate 13 side in the extending direction, in other words, toward the side opposite to the motor 20. The main plate 11 further includes a flat portion 17, and the flat portion 17 is provided so as to surround the convex portion 16 in the radial direction and extends in a direction perpendicular to the rotation axis. The outer peripheral end 11b is configured as an outer peripheral end of the flat portion 17, for example. The convex portion 16 and the flat portion 17 are integrally provided. The boundary between the convex portion 16 and the flat portion 17 is a connection point between the outer peripheral end portion of the convex portion 16 whose end surface forms a curve in a cross section along the rotation shaft 21 and the inner peripheral end portion of the flat portion 17 whose end surface forms a plane.
The convex portion 16 has a top portion disposed at a position farthest from the flat portion 17 in the extending direction and the radial direction, and an outer peripheral end portion as a bottom portion connected to an inner peripheral end portion of the flat portion 17. A boss portion 30 fixed to the rotary shaft 21 is attached to the top of the protruding portion 16. Thus, the main plate 11 is fixed to the rotary shaft 21 via the boss portion 30.
The flat portion 17 is provided in a ring shape along the circumferential direction. The flat portion 17 has an inner peripheral end connected to the outer peripheral end of the convex portion 16 and an outer peripheral end forming the outer peripheral end 11b of the main plate 11.
The convex portion 16 has a convex surface 16a and a concave surface 16b, the convex surface 16a protruding with respect to the flat portion 17 when the main plate 11 is viewed from the side plate 13 side, and the concave surface 16b being disposed on the opposite side to the convex surface 16a and recessed with respect to the flat portion 17 when the main plate 11 is viewed from the opposite side to the side plate 13 side. The convex portion 16 has a concave portion 19, and the concave portion 19 is surrounded by a concave surface 16b at a position further inward than the flat portion 17 when the main plate 11 is viewed from the side opposite to the side plate 13.
The convex surface 16a has, for example, a first curved surface 16aa, a second curved surface 16ab, and a conical surface 16ac. The first curved surface 16aa is disposed on the suction port 14 side of the conical surface 16ac in the extending direction, and is disposed on the inner peripheral side of the conical surface 16ac in the radial direction. The second curved surface 16ab is disposed on the side of the conical surface 16ac closer to the air outlet 15 in the extending direction, and is disposed on the outer peripheral side of the conical surface 16ac in the radial direction.
The radially inner peripheral end portion of the first curved surface 16aa is connected to the hub portion 30, for example. The radially outer peripheral end of the first curved surface 16aa is connected to, for example, the radially inner peripheral end of the conical surface 16ac. The radially outer peripheral end of the conical surface 16ac is connected to, for example, the radially inner peripheral end of the second curved surface 16 ab. The radial outer peripheral end of the second curved surface 16ab is connected to, for example, the inner peripheral end of the flat portion 17. The boundary between the first curved surface 16aa and the conical surface 16ac is a connection point between the outer peripheral end portion of the first curved surface 16aa, which forms a curve at the end surface in a cross section along the rotation axis 21, and the inner peripheral end portion of the conical surface 16ac, which forms a straight line at the end surface. The boundary between the conical surface 16ac and the second curved surface 16ab is a connection point between the outer peripheral end portion of the conical surface 16ac, in which the end surface forms a straight line in the cross section along the rotation axis 21, and the inner peripheral end portion of the second curved surface 16ab, in which the end surface forms a curved line.
The first curved surface 16aa is provided in a convex shape when the main plate 11 is viewed from the side plate 13 side. The second curved surface 16ab is provided in a concave shape when the main plate 11 is viewed from the side plate 13 side. The conical surface 16ac is a conical surface centered on the rotation axis 21. The center of curvature of the first curved surface 16aa is disposed on the concave surface 16b side with respect to the main plate 11. In other words, the center of curvature of the first curved surface 16aa is disposed on the opposite side of the first curved surface 16aa from the suction port 14 in the extending direction. The center of curvature of the second curved surface 16ab is disposed on the convex surface 16a side with respect to the main plate 11. In other words, the center of curvature of the second curved surface 16ab is disposed closer to the suction port 14 than the second curved surface 16ab in the radial direction.
The plurality of blades 12 are disposed between the main plate 11 and the side plate 13. Each blade 12 connects, for example, the flat portion 17 of the main plate 11 and the side plate 13. The blades 12 are arranged at intervals in the circumferential direction. The inner peripheral end of each blade 12 is disposed, for example, on the outer peripheral side of the outer peripheral end of the convex portion 16.
The side plate 13 is provided in a ring shape along the circumferential direction. The side plate 13 has an inner peripheral end portion 13a provided to form the suction port 14 of the centrifugal fan 10 and an outer peripheral end portion 13b provided to form the blow-out port 15 with the main plate 11. The inner peripheral end portion 13a is disposed at a position farther from the flat portion 17 of the main plate 11 than the outer peripheral end portion 13b in the extending direction. In a cross section along the rotation shaft 21, the side plate 13 has a curved shape in which a curvature center is arranged on the outer peripheral side of the side plate 13 in the radial direction. Each blade 12 is connected to the outer peripheral end portion 13b of the side plate 13 from, for example, a portion of the side plate 13 located closer to the flat portion 17 than the inner peripheral end portion 13 a. The inner peripheral end portions of the blades 12 are disposed, for example, on the inner peripheral side of the inner peripheral end portion 13a of the side plate 13.
The suction port 14 is an opening surrounded by the inner peripheral end 13a of the side plate 13. When the centrifugal fan 10 is viewed from the extending direction, the plane shape of the suction port 14 is a circle centered on the rotation axis 21. The centrifugal fan 10 has a plurality of outlets 15 arranged in a row in the circumferential direction. Each of the air outlets 15 is arranged between the outer peripheral end 11b of the main plate 11 and the outer peripheral end 13b of the side plate 13 in the extending direction, and between the adjacent 2 blades 12 in the circumferential direction.
As described above, the rotary shaft 21 of the motor 20 is fixed to the main plate 11 of the centrifugal fan 10 via the boss portion 30. The driving unit 22 houses therein a stator and a rotor that rotates together with the rotary shaft 21 with respect to the stator. The driving portion 22 has a portion accommodated in the concave portion 19 surrounded by the concave surface 16b of the main plate 11. The driving portion 22 includes, for example, a first portion accommodated in the recess and a second portion disposed outside the recess. The first portion and the second portion are arranged in the extending direction.
The support portion 23 is disposed on the outer side of the drive portion 22 in the radial direction, and is fixed to at least one of the first portion and the second portion of the drive portion 22. The support portion 23 includes, for example, a portion accommodated in the recess and a portion disposed outside the recess. The support portion 23 is fixed to a housing of the blower 100, not shown, by a fixing member, not shown. A heat exchanger, not shown, is fixed to the housing. The heat exchanger is disposed so as to face the air outlet 15 in the radial direction.
As shown in fig. 2, the longest distance in the extending direction between the top and bottom of the convex surface 16a of the convex portion 16 is referred to as the height a of the convex portion 16 relative to the flat portion 17 of the main plate 11. The longest distance in the extending direction between the outer peripheral end 11b of the flat portion 17 of the main plate 11 and the outer peripheral end 13b of the side plate 13 is equal to the width b of the air outlet 15 in the extending direction. The ratio a/b of the height a to the width b is less than 1/2. Preferably, the above ratio a/b is less than 1/3. The width b of the outlet 15 in the extending direction is, for example, equal to or less than the width of the heat exchanger disposed opposite to the outlet 15 in the radial direction in the extending direction.
As shown in fig. 2, the width c of the first portion of the driving portion 22 disposed in the recess 19 in the extending direction is wider than half the width d of the driving portion 22 in the extending direction. In other words, the width c is wider than the width m (i.e., the difference between the width d and the width c) in the extending direction of the second portion of the driving portion 22 disposed outside the concave portion 19. The width m may be zero. In other words, the entire driving portion 22 may be disposed inside the recess 19. In this case, the width c is greater than zero as the width of the entire driving portion 22 in the extending direction.
As shown in fig. 2, the longest distance between the inner peripheral end portions 13a of the side plates 13 disposed opposite to each other in the radial direction is referred to as the inner diameter e of the suction port 14. The longest distance between the outer peripheral ends of the convex portions 16 arranged in the radial direction with the rotation shaft 21 interposed therebetween is referred to as the width f of the convex portions 16. The inner diameter e of the suction port 14 is larger than the width f of the projection 16, for example. The height a of the convex portion 16 is, for example, not less than half of the width f of the convex portion 16 and not more than the width f. The width b is smaller than the inner diameter e.
The use of the blower 100 is not particularly limited, and is, for example, suitable for a blower that is disposed in an indoor unit of an air conditioner and blows air to an indoor heat exchanger. In this case, the heat exchanger is disposed at a position facing the air outlet 15 in the radial direction, for example (see fig. 8).
< Effect >
The blower 100 includes a motor 20 and a centrifugal fan 10, the motor 20 including a rotation shaft 21 and a driving unit 22 for rotating the rotation shaft 21, and the centrifugal fan 10 including: a main plate 11 fixed to the rotation shaft 21; an annular side plate 13 disposed at a distance from the main plate 11 in the extending direction; and a plurality of blades 12 arranged between the main plate 11 and the side plate 13, and the centrifugal fan 10 is rotated by a motor 20. An opening portion forming the suction port 14 of the centrifugal fan 10 is provided in the center of the side plate 13 in the radial direction. The main plate 11 has a convex portion 16, and the convex portion 16 is arranged at the center in the radial direction and is convex toward the suction port 14 in the extending direction when the main plate 11 is viewed from the side plate 13 side. A blowout port 15 of the centrifugal fan 10 is provided between the outer peripheral end 11b of the main plate 11 and the outer peripheral end 13b of the side plate 13. The convex portion 16 has a convex surface 16a provided to be convex when the main plate 11 is viewed from the side plate 13 side, and a concave surface 16b arranged on the opposite side to the convex surface 16 a. At least a part of the driving portion 22 is accommodated in the concave portion 19 surrounded by the concave surface 16b. The height a of the projection 16 in the extending direction is smaller than half the width b of the air outlet 15 in the extending direction. The width c of the portion of the driving portion 22 disposed inside the recess 19 in the extending direction is wider than half the width d of the driving portion 22 in the extending direction.
When the ratio a/b is 1/2 or more, the air volume on the main plate 11 side in the extending direction between the plurality of blades 12 decreases, and the air flowing into the outer peripheral side of the suction port 14 is less likely to flow along the side plate 13. Therefore, the wind speed distribution between the blades 12 becomes uneven, and the ventilation resistance between the blades 12 increases. Fig. 3 is a graph showing a relationship between the ratio a/b and electric power (hereinafter referred to as a fan input) supplied to the blower so that the air volume blown out from the blower reaches a set air volume. The horizontal axis of FIG. 3 represents the ratio a/b, and the vertical axis of FIG. 3 represents normalized fan input. As shown in fig. 3, when the ratio a/b is 1/2 or more, the fan input increases and the air blowing efficiency decreases as compared with the case where the ratio a/b is less than 1/2. In this case, the noise of the blower also increases.
If the ratio a/b is smaller than 1/2 by decreasing the height a, the width m becomes larger than the width c, and the blower 100 becomes larger in the extending direction. Further, by increasing the width b to make the ratio a/b smaller than 1/2, the blower 100 is also enlarged in the extending direction.
In contrast, in the blower 100, the ratio a/b is smaller than 1/2, and the width c is wider than half of the width d. Accordingly, as shown in fig. 3, in the blower 100, the fan input is reduced, the blower efficiency is improved, and the noise is reduced, as compared with the case where the ratio a/b is 1/2 or more.
Further, since the width m is smaller than the width c, the blower 100 is prevented from increasing in size in the extending direction. By forming the convex portion 16 and the motor 20 into flat shapes, the blower 100 having the ratio a/b of less than 1/2 and the width c of less than half the width d is realized. The flattening of the motor 20 is achieved, for example, by disposing the support portion 23 of the motor 20 at a position radially outside the drive portion 22, as compared with a motor fixed to the blower without the support portion 23. For this reason, in the blower 100, a decrease in the blower efficiency, an increase in noise, and an increase in size are suppressed.
Preferably, the above ratio a/b is less than 1/3. In this way, the wind speed distribution in the extending direction between the blades 12 is more uniform, the ventilation resistance between the blades 12 is reduced, and the fan input is further reduced, as compared with the case where the ratio a/b is 1/3 or more and less than 1/2.
Embodiment 2
As shown in fig. 4, the blower 101 of embodiment 2 has substantially the same structure as the blower 100 of embodiment 1, but is different in that the height a of the convex portion 16 is smaller than half the width f of the convex portion 16.
The longest distance in the extending direction between the top and bottom of the concave surface 16b of the convex portion 16 is smaller than half the width f of the convex portion 16. The inner diameter e of the suction port 14 is larger than the width f of the projection 16.
When comparing the blower 100 having the height a of the convex portion 16 which is half or more of the width f of the convex portion 16 and the blower 101 having the inner diameter e equal to the blower 100, the convex portion 16 of the blower 101 is flattened than the convex portion 16 of the blower 100.
In the blower 101, the height a is smaller than half of the width f of the convex portion 16, and therefore, the convex portion 16 is provided to be flatter than in the case where the height a is equal to or larger than half of the width f of the convex portion 16. Therefore, in the blower 101, the height a is smaller than the case where the height a is half or more of the width f of the convex portion 16, but the volume of the concave portion 19 of the blower 101 is larger. As a result, in the blower 101, a decrease in blower efficiency, an increase in noise, and an increase in size are further suppressed as compared with a case where the height a is half or more of the width f of the convex portion 16 in the blower 100.
Embodiment 3
As shown in fig. 5, the blower 102 of embodiment 3 has substantially the same configuration as the blower 100 of embodiment 1, but differs in that the radial width h of the first curved surface 16aa is wider than the radial width i of the second curved surface 16 ab. The blower 102 may have the same configuration as the blower 101, as long as the radial width h of the first curved surface 16aa is wider than the radial width i of the second curved surface 16 ab.
The radius of curvature of the first curved surface 16aa is larger than the radius of curvature of the second curved surface 16 ab. The width h of the first curved surface 16aa is smaller than the radial width j of the conical surface 16ac, for example. The sum of the width h of the first curved surface 16aa, the width i of the second curved surface 16ab, and the sum of the width j of the conical surface 16ac, which is 2 times the width of the boss portion 30 in the radial direction, is equal to the width f of the convex portion 16.
In the blower 102, the width h is larger than the width i, and therefore, the gas flowing from the suction port 14 to the vicinity of the top of the convex portion 16 smoothly flows along the first curved surface 16aa and the conical surface 16ac. This makes it difficult to peel off the air flow on the first curved surface 16aa and the conical surface 16ac. The gas flowing along the conical surface 16ac is deflected along the second curved surface 16ab, and flows into the main plate 11 side in the extending direction between the blades 12. As a result, the air volume on the main plate 11 side in the extending direction increases, the wind speed distribution between the blades 12 becomes uniform, and the ventilation resistance between the blades 12 decreases, as compared with the case where the width h is smaller than the width i. As a result, in the blower 102, the blower efficiency is further improved and the noise is further reduced, as compared with the case where the width h is narrower than the width i in the blower 100.
When the width h of the first curved surface 16aa is smaller than the radial width j of the conical surface 16ac, even when the peeling of the air flow occurs in the first curved surface 16aa, so-called reattachment of the peeled air flow along the conical surface 16ac occurs easily. Accordingly, the blower 102 having the width h smaller than the width j has a higher blower efficiency than the blower 102 having the width h not smaller than the width j.
Embodiment 4
As shown in fig. 6, the blower 103 of embodiment 4 has substantially the same structure as the blower 100 of embodiment 1, but differs in that the outer peripheral end 11b of the main plate 11 and the outer peripheral end 13b of the side plate 13 are bent toward the side opposite to the suction port 14 in the extending direction. The blower 103 may have the same structure as the blower 101 or the blower 102, as long as the outer peripheral end 11b of the main plate 11 and the outer peripheral end 13b of the side plate 13 are bent toward the opposite side to the suction port 14 in the extending direction.
The main plate 11 has, for example, a convex portion 16, a flat portion 17, and a first curved portion 18 curved toward the opposite side of the suction port 14 with respect to the flat portion 17. The inner peripheral end of the flat portion 17 is connected to the outer peripheral end of the convex portion 16. The radially outer peripheral end of the flat portion 17 is connected to the radially inner peripheral end of the first curved portion 18. The radial outer peripheral end portion of the first curved portion 18 forms an outer peripheral end portion 11b of the main plate 11. In a cross section along the rotation shaft 21, the center of curvature of the first curved portion 18 is disposed on the inner peripheral side of the outer peripheral end portion 11b in the radial direction.
The side plate 13 has, for example, a second bent portion 24 having an inner peripheral end portion 13a of the side plate 13 and a third bent portion 25 having an outer peripheral end portion 13b of the side plate 13, the second bent portion 24. In a cross section along the rotation shaft 21, the center of curvature of the second bending portion 24 is disposed on the outer peripheral side of the inner peripheral end portion 13a of the side plate 13 in the radial direction. In a cross section along the rotation shaft 21, the center of curvature of the third bending portion 25 is disposed on the inner peripheral side of the outer peripheral end portion 13b of the side plate 13 in the radial direction.
The inner peripheral ends of the plurality of blades 12 are arranged between the flat portion 17 of the main plate 11 and the second curved portion 24 of the side plate 13. The outer peripheral ends of the plurality of blades 12 are arranged between the outer peripheral end 11b of the main plate 11 and the outer peripheral end 13b of the side plate 13. That is, a part of the plurality of blades 12 on the side of the blowout port 15 is arranged between the first curved portion 18 and the third curved portion 25. The interval in the extending direction between the first curved portion 18 and the third curved portion 25 is set to be constant, for example.
In the blower 103, the outer peripheral end 11b of the main plate 11 and the outer peripheral end 13b of the side plate 13 are bent toward the side opposite to the suction port 14 in the extending direction, and therefore, the blower 103 can smoothly blow out the gas toward the side opposite to the suction port 14 in the extending direction. Therefore, the blower 103 is suitable for a unit requiring the air path AF along the extending direction on the downstream side of the blower. In the air passage along the extending direction formed downstream of the blower 103, the deviation of the air flow is reduced and the pressure loss is reduced as compared with the air passage in the blower in which the outer peripheral end 11b of the main plate 11 and the outer peripheral end 13b of the side plate 13 are not bent toward the side opposite to the suction port 14 in the extending direction. As a result, the blower 103 has a higher blower efficiency when used in the unit than when used in the unit, in which the outer peripheral end portion 11b and the outer peripheral end portion 13b are not bent toward the opposite side of the suction port 14 in the extending direction.
Embodiment 5
As shown in fig. 7, the blower 104 of embodiment 5 has substantially the same structure as the blower 100 of embodiment 1, but is different in that, in a cross section along the rotation axis 21, a first region R1 in which the distance between the main plate 11 and the side plate 13 on a straight line perpendicular to the side plate 13 gradually decreases from the suction port 14 toward the blow-out port 15 and a second region R2 arranged on the blow-out port 15 side of the first region R1 are provided in the centrifugal fan 10, and in that, in the second region R2, the distance between the main plate 11 and the side plate 13 on a straight line perpendicular to the side plate 13 gradually increases from the suction port 14 toward the blow-out port 15. In addition, the blower 104 is smaller than half the width f of the convex portion 16 in the height a of the convex portion 16, as in the blower 101.
The first region R1 is formed in the side plate 13 between, for example, a portion on the inner peripheral end portion 13a side of a connection portion with the inner peripheral end portions of the plurality of blades 12 and a portion on the outer peripheral end portion 13b side of the connection portion.
The first region R1 is formed, for example, between a first straight line perpendicular to a portion of the side plate 13 located closer to the suction port 14 than a connection portion with the inner peripheral end portions of the plurality of blades 12, and a second straight line perpendicular to a portion of the side plate 13 located closer to the blowout port 15 than the connection portion. The distance k between the main plate 11 and the side plate 13 on the first straight line is longer than the distance l between the main plate 11 and the side plate 13 on the second straight line. In the first region R1, the distance between the main plate 11 and the side plate 13 on a line perpendicular to the side plate 13 is not less than the distance l and not more than the distance k, and gradually decreases from the suction port 14 toward the discharge port 15.
The second region R2 is disposed closer to the air outlet 15 than the first region R1. The second region R2 is disposed in a manner connected to the first region R1. The second region R2 is formed between the outer peripheral end portion 13b and a portion of the side plate 13 located closer to the outer peripheral end portion 13b than a connection portion with the inner peripheral end portions of the plurality of blades 12, for example.
The second region R2 is formed, for example, between the second straight line and a third straight line perpendicular to the outer peripheral end portion 13b of the side plate 13. The distance l between the main plate 11 and the side plate 13 on the second straight line is shorter than the distance between the main plate 11 and the side plate 13 on the third straight line. The distance between the main plate 11 and the side plate 13 on the third straight line is equal to the width b, for example. In the second region R2, the distance between the main plate 11 and the side plate 13 on a line perpendicular to the side plate 13 is not less than the distance l and not more than the distance b, and gradually increases from the suction port 14 toward the discharge port 15.
A part of the plurality of blades 12 located on the suction port 14 side is arranged in a region located on the blow-out port 15 side in the first region R1. The remaining portions of the plurality of blades 12 on the side of the blowout port 15 are disposed in the second region R2.
In the blower 104, the air flowing into the centrifugal fan 10 from the suction port 14 flows through the first region R1 and the second region R2 in this order, and reaches the discharge port 15. In other words, the gas flowing from the suction port 14 flows in the region located on the suction port 14 side in the first region R1, and then reaches between the blades 12. In the first region R1, the distance between the main plate 11 and the side plate 13 on a line perpendicular to the side plate 13 gradually decreases from the suction port 14 toward the discharge port 15, and therefore, the gas flowing between the blades 12 is stable, and the gas flow in the vicinity of the inner peripheral end portions of the blades 12 is less likely to peel off. In the second region R2, the distance between the main plate 11 and the side plate 13 on a line perpendicular to the side plate 13 gradually increases from the suction port 14 toward the discharge port 15, and therefore, the gas flowing in the second region R2 is boosted by the diffuser effect. As a result, the blower 104 has a blower efficiency that is further improved than that of the blower 100.
In addition, the height a is smaller than half the width b, and therefore, the wind speed distribution between the main plate 11 and the side plate 13 at the air outlet 15 is uniform, as in the case of the blower 100. Therefore, in the second region R2 which exhibits the diffuser effect, peeling of the air flow on the side plate 13 is not easily generated. Accordingly, the blower 104 has an improved blower efficiency compared to a blower having a centrifugal fan with only a diffuser shape.
Embodiment 6
As shown in fig. 8, the blower 105 of embodiment 6 has substantially the same structure as the blower 100 of embodiment 1, but differs in that the width b is one half or more of the width n in the extending direction of the heat exchanger 40 arranged opposite to the air outlet 15 in the radial direction. The blower 105 may have the same configuration as any one of the blowers 101 to 104, provided that the width b is equal to or more than half the width n.
The blower 105 is provided in the indoor unit 200. The indoor unit 200 includes the blower 105, the heat exchanger 40, and the casing 50. The indoor unit 200 is, for example, a ceiling-embedded indoor unit. The extending direction of the blower 105 is along the up-down direction, and the radial direction is along the horizontal direction. The suction port 14 opens downward.
The heat exchanger 40 is disposed so as to face the air outlet 15 in the radial direction of the blower 105.
The casing 50 houses the blower 105 and the heat exchanger 40 therein. The support 23 of the blower 105 is fixed to the housing 50 by the fixing member 31. An opening for introducing indoor air into the suction port 14 is provided below the suction port 14 of the blower 105 in the housing 50. A grill 51 is attached to the opening. In the radial direction, a plurality of air outlets 52 are provided on the outer side of the grill 51, and the plurality of air outlets 52 are configured to blow out air, which has been heat-exchanged with the refrigerant in the heat exchanger 40, from the air outlet 15 of the blower 105 into the room. The heat exchanger 40 is disposed between the outlet 15 and the outlet 52 of the blower 105 in the housing 50. The upper end of the heat exchanger 40 is connected to the frame 50. The lower end of the heat exchanger 40 is connected to a drain pan 53.
The width b of the blower 105 is equal to or more than half of the width n of the heat exchanger 40 arranged to face the air outlet 15 in the radial direction in the extending direction. The width b is not more than the width n. The outer peripheral end 11b of the main plate 11 of the blower 105 is disposed above the central portion of the heat exchanger 40 in the extending direction, for example. The outer peripheral end portion 13b of the side plate 13 of the blower 105 is disposed, for example, below the central portion of the heat exchanger 40 in the extending direction.
In the extending direction, the outer peripheral end portion 13b of the side plate 13 is disposed closer to the center of the heat exchanger 40 than the drain pan 53.
The height a is smaller than half the width b, and therefore, the wind velocity distribution between the main plate 11 and the side plate 13 at the air outlet 15 is uniform, as in the case of the blower 100. Therefore, even if the width b is relatively large, which is half or more of the width n of the heat exchanger 40, the air flow on the side plate 13 is less likely to be peeled off.
In the blower 105, the difference between the width b and the width n is smaller than the case where the width b of the air outlet 15 is smaller than half the width n of the heat exchanger, and therefore, the wind speed distribution in the heat exchanger 40 is uniformed, and the pressure loss of the gas is reduced.
In the blower 105, the outer peripheral end portion 13b of the side plate 13 is disposed closer to the center of the heat exchanger 40 than the drain pan 53 in the extending direction. Therefore, in the indoor unit 200 provided with the blower 105, the air blown out from the air outlet 15 is less likely to collide with the drain pan 53, and therefore, the increase in ventilation resistance in the indoor unit 200 is suppressed.
The indoor unit 200 provided with the blower 105 suppresses a decrease in blower efficiency, an increase in noise, and an increase in size, as compared with the indoor unit provided with the conventional blower.
As shown in fig. 9, blowers 100 to 105 according to embodiments 1 to 6 can be applied to an air conditioner 300. The air conditioner 300 includes, for example, an indoor unit 200 and an outdoor unit 210. The indoor unit 200 includes the heat exchanger 40 and the blowers 100 to 105. The outdoor unit 210 includes a compressor 211, an outdoor heat exchanger 212, an expansion valve 213, a four-way valve 214, and an outdoor blower 215. The indoor unit 200 and the outdoor unit 210 are connected to each other via a plurality of refrigerant pipes, and the indoor unit 200, the outdoor unit 210, and the plurality of refrigerant pipes constitute a refrigerant circuit including a compressor 211, an outdoor heat exchanger 212, an expansion valve 213, a four-way valve 214, and a heat exchanger 40. From a different point of view, the air conditioner 300 includes: at least 1 blower 100 to 105; an air path provided downstream of the air outlets 15 of the at least 1 blowers 100 to 105; and a heat exchanger 40 disposed in the air passage. In the air conditioner 300, the blowers 100 to 105 are used as blowers for blowing air to an indoor heat exchanger in an indoor unit, for example. The indoor unit 200 including the blowers 100, 101, 103 to 105 has the same configuration as the indoor unit 200 shown in fig. 8, for example. In the indoor unit 200 including the blower 102, for example, an air passage provided downstream of the air outlet 15 extends in the extending direction toward the opposite side of the air inlet 14 with respect to the air outlet 15, and the heat exchanger 40 is disposed in the air passage.
While the embodiments of the present invention have been described above, various modifications may be made to the above-described embodiments. The scope of the present invention is not limited to the above-described embodiments. The scope of the present invention is indicated by the claims, and all changes that come within the meaning and range of equivalency of the claims are intended to be embraced therein.
Description of the reference numerals
A centrifugal fan 10, a main plate 11, outer peripheral ends of 11b and 13b, a blade 12, a side plate 13, an inner peripheral end of 13a, a suction inlet 14, a suction outlet 15, a suction outlet 52, a convex portion 16a, a convex portion 16aa, a first curved surface 16aa, a second curved surface 16ab, a concave portion 16b, a flat portion 17, a first curved portion 18, a concave portion 19, a motor 20, a rotating shaft 21, a driving portion 22, a supporting portion 23, a second curved portion 24, a third curved portion 25, a hub portion 30, a fixing member 31, a heat exchanger 40, a frame 50, a grille 51, a drain tray 53, a blower 100, 101, 102, 103, 104, 105, a fan 200 indoor unit 200, and an air conditioner 300.
Claims (8)
1. A blower is provided with:
a motor including a rotation shaft and a driving part that rotates the rotation shaft; and
a centrifugal fan, the centrifugal fan comprising: a main plate fixed to the rotation shaft; an annular side plate disposed at a distance from the main plate in the extending direction of the rotary shaft; and a plurality of blades disposed between the main plate and the side plate, the centrifugal fan being rotated by the motor,
in the centrifugal fan, a blow-out port is provided between an outer peripheral end portion of the main plate in a radial direction with respect to the rotation shaft and an outer peripheral end portion of the side plate in the radial direction,
the main plate has a convex portion which is arranged at the center in the radial direction and is convex toward the side plate side in the extending direction,
the convex portion has a convex surface provided in a convex shape and a concave surface arranged on the opposite side to the convex surface,
at least a part of the driving part is arranged in the concave part surrounded by the concave surface,
the height a of the protruding portion in the extending direction is smaller than half the width b of the blow-out port in the extending direction,
the width c of the at least one portion of the driving portion disposed in the recess in the extending direction is wider than half of the width d of the driving portion in the extending direction,
the main plate is fixed to the rotating shaft via a boss portion mounted on the top of the boss portion,
the centrifugal fan is provided with a suction port surrounded by the inner peripheral end of the side plate in the radial direction relative to the rotation shaft,
in a section along the rotation axis, the centrifugal fan is provided with: a first region in which a distance between the main plate and the side plate on a straight line perpendicular to the side plate gradually decreases from the suction port toward the blowout port; and a second region disposed closer to the air outlet than the first region, wherein a distance between the main plate and the side plate on a straight line perpendicular to the side plate in the second region gradually increases from the air inlet toward the air outlet,
the first region is formed between a first straight line perpendicular to a portion of the side plate on the suction port side of a connection portion connected to inner peripheral end portions of the plurality of blades, and a second straight line perpendicular to a portion of the side plate on the blowout port side of the connection portion, and the second region is formed between the second straight line and a third straight line perpendicular to the outer peripheral end portions of the side plate.
2. The blower according to claim 1, wherein,
the inner diameter e of the suction port is larger than the radial width f of the convex part,
the height a is less than half the width f,
the plurality of blades have inner peripheral end portions arranged at positions outside the convex portions in the radial direction.
3. The blower according to claim 1 or 2, wherein,
in a cross section along the rotation axis, the convex surface of the convex portion has: a conical surface centered on the rotation axis; a first curved surface disposed closer to the suction port than the conical surface; and a second curved surface arranged closer to the air outlet than the conical surface,
the first curved surface is provided in a convex shape and the second curved surface is provided in a concave shape when the main plate is viewed from the side plate side,
the radial width h of the first curved surface is wider than the radial width i of the second curved surface.
4. The blower according to claim 1 or 2, wherein,
the outer peripheral end portion of the main plate and the outer peripheral end portion of the side plate are curved toward a side opposite to the suction port in the extending direction.
5. The blower according to claim 3, wherein,
the outer peripheral end portion of the main plate and the outer peripheral end portion of the side plate are curved toward a side opposite to the suction port in the extending direction.
6. An indoor unit, comprising:
the blower of any one of claims 1 to 5;
a heat exchanger disposed opposite to the air outlet in the radial direction,
the width b is half or more of the width n of the heat exchanger in the extending direction.
7. The indoor unit of claim 6, wherein,
further comprises a drain pan connected to one end of the heat exchanger in the extending direction,
in the extending direction, the outer peripheral end portion of the side plate is disposed closer to the center of the heat exchanger than the drain pan.
8. An air conditioner, comprising:
the blower of any one of claims 1 to 5; and
and a heat exchanger disposed in the air passage downstream of the air outlet of the blower.
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| PCT/JP2019/001661 WO2020152748A1 (en) | 2019-01-21 | 2019-01-21 | Fan blower, indoor unit, and air conditioner |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN113302401A CN113302401A (en) | 2021-08-24 |
| CN113302401B true CN113302401B (en) | 2023-08-18 |
Family
ID=71736594
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201980088500.6A Active CN113302401B (en) | 2019-01-21 | 2019-01-21 | Blower, indoor unit and air conditioner |
Country Status (4)
| Country | Link |
|---|---|
| EP (1) | EP3916238A4 (en) |
| JP (1) | JP7086229B2 (en) |
| CN (1) | CN113302401B (en) |
| WO (1) | WO2020152748A1 (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114321008A (en) * | 2022-01-19 | 2022-04-12 | 雷沃工程机械集团有限公司 | Fan device |
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| JPH09228992A (en) * | 1996-02-23 | 1997-09-02 | Hitachi Ltd | Blower device |
| EP0882185A1 (en) * | 1996-12-11 | 1998-12-09 | Carrier Corporation | Fan and motor assembly for an air conditioner |
| JP2000146214A (en) * | 1998-11-02 | 2000-05-26 | Matsushita Refrig Co Ltd | Air conditioner |
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| CN1664376A (en) * | 2004-03-05 | 2005-09-07 | 松下电器产业株式会社 | Blower |
| KR20070099367A (en) * | 2006-04-04 | 2007-10-09 | 엘지전자 주식회사 | Cassette type air conditioner |
| CN201475038U (en) * | 2009-09-03 | 2010-05-19 | 上海诺地乐通用设备制造有限公司 | Fully-mixed flow impeller |
| JP2015040479A (en) * | 2013-08-20 | 2015-03-02 | 株式会社デンソー | Blower |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| JP2000314391A (en) * | 1999-03-03 | 2000-11-14 | Mitsubishi Electric Corp | Scirocco fan, molten metal forming method for the scirocco fan, molten metal forming device for the scirocco fan |
| JP2005133710A (en) * | 2003-10-07 | 2005-05-26 | Daikin Ind Ltd | Centrifugal blower and air conditioner using it |
| WO2006126408A1 (en) | 2005-05-26 | 2006-11-30 | Toshiba Carrier Corporation | Centrifugal blower and air conditioner using the same |
| FR3007086B1 (en) * | 2013-06-18 | 2015-07-03 | Cryostar Sas | CENTRIFUGAL WHEEL |
| DE102017100684A1 (en) * | 2017-01-16 | 2018-07-19 | Ebm-Papst Mulfingen Gmbh & Co. Kg | Fan wheel with predefined discharge direction |
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2019
- 2019-01-21 EP EP19910985.1A patent/EP3916238A4/en active Pending
- 2019-01-21 CN CN201980088500.6A patent/CN113302401B/en active Active
- 2019-01-21 JP JP2020567680A patent/JP7086229B2/en active Active
- 2019-01-21 WO PCT/JP2019/001661 patent/WO2020152748A1/en unknown
Patent Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH09228992A (en) * | 1996-02-23 | 1997-09-02 | Hitachi Ltd | Blower device |
| EP0882185A1 (en) * | 1996-12-11 | 1998-12-09 | Carrier Corporation | Fan and motor assembly for an air conditioner |
| JP2000146214A (en) * | 1998-11-02 | 2000-05-26 | Matsushita Refrig Co Ltd | Air conditioner |
| CN1280254A (en) * | 1999-03-03 | 2001-01-17 | 三菱电机株式会社 | Multiple blade fan, forming method and device for producing melting metal thereof |
| CN1664376A (en) * | 2004-03-05 | 2005-09-07 | 松下电器产业株式会社 | Blower |
| KR20070099367A (en) * | 2006-04-04 | 2007-10-09 | 엘지전자 주식회사 | Cassette type air conditioner |
| CN201475038U (en) * | 2009-09-03 | 2010-05-19 | 上海诺地乐通用设备制造有限公司 | Fully-mixed flow impeller |
| JP2015040479A (en) * | 2013-08-20 | 2015-03-02 | 株式会社デンソー | Blower |
Also Published As
| Publication number | Publication date |
|---|---|
| CN113302401A (en) | 2021-08-24 |
| EP3916238A1 (en) | 2021-12-01 |
| WO2020152748A1 (en) | 2020-07-30 |
| EP3916238A4 (en) | 2022-01-19 |
| JP7086229B2 (en) | 2022-06-17 |
| JPWO2020152748A1 (en) | 2021-10-14 |
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