JP2012107561A - Fan - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a fan having a uniform flow velocity distribution at an exhaust port and contributing to noise reduction when incorporated into an actual machine.SOLUTION: The fan comprises an impeller 1 and a casing 2 having a suction port 7 provided in an axial direction of the impeller 1 and an exhaust port provided in an outer circumferential direction of the impeller 1. A first flow straightening plate 15 is positioned at an intermediate part in the axial direction of the impeller 1 and disposed downward toward the outer circumference of the impeller 1. In this way, some of a wind sucked from the suction port 7 with the rotation of the impeller 1 may be also guided to the exhaust port from the upper side of the impeller 1 by the first flow straightening plate 15. Further, the rest of the wind is lead to the lower side of the impeller 1 with the first flow straightening plate 15 in between, and is guided to the exhaust port without largely hindering the flow of the wind.

Description

  The present invention relates to a fan that blows air by rotating an impeller.

  Conventionally, in this type of fan, in order to improve the cooling performance and noise performance in actual use, the blade shape has been designed on the assumption that a duct having desired characteristics is installed at the customer site. (For example, patent document 1).

  Further, in a conventional sirocco fan, for example, as shown in FIG. 11, an impeller 105 including a shroud 102 on one side, a shroud 103 on the other side, a blade 104, and the like is rotatably disposed in a casing 101 that forms the outer shell of the fan. The blades 104 are arranged vertically with respect to the one-side shroud 102 and the other-side shroud 103. Such an arrangement structure of the blades 105 is also shown in Patent Document 2, for example.

JP 2006-54250 A JP 2008-215324 A

  However, in the above prior art, the fan blade shape itself is formed by a single blade, and does not have a structure for uniformly distributing the air taken from the intake port. For this reason, the flow velocity distribution differs at the exhaust port of the fan, and a difference in cooling performance and noise is caused by the duct as an actual machine incorporated at the customer site.

  In the example of FIG. 11, an air flow S is formed in the casing 101 in the direction of the arrow as the impeller 105 and the blade 104 rotate, but a part of the air flow S toward the one-side shroud 102 is formed. However, without being sucked into the impeller 105, it is guided to the upper surface side in the casing 101, and the offset vortex S 'is generated there, causing noise.

  SUMMARY OF THE INVENTION Accordingly, a first object of the present invention is to provide a fan that can make the flow velocity distribution at the exhaust port uniform and contribute to noise reduction when incorporated in an actual machine.

  It is a second object of the present invention to provide a fan capable of adjusting the air flow distribution accompanying the rotation of the blades and reducing noise.

  In the first aspect of the invention, a part of the wind sucked from the intake port can be guided to the exhaust port from the side toward the intake port of the impeller by the first rectifying plate, and the remaining wind is sandwiched between the first rectifying plate. Thus, the air can be guided to the side opposite to the intake port of the impeller and guided to the exhaust port without significantly impeding the flow of the wind. As a result, the flow of wind can be adjusted appropriately on one side and the other side of the first rectifying plate, and the flow velocity distribution at the exhaust port can be made uniform.

  In the invention of claim 2, if the height of the boss part is suppressed to 2/3 or less of the blade height, the resistance of the boss part against the flow of air from the air inlet to the blade can be reduced, and noise during incorporation in the actual machine Can be further reduced.

  In the invention of claim 3, by providing another second rectifying plate also inside the casing, the flow velocity distribution in the axial direction of the impeller can be improved, and the flow velocity distribution in the outer peripheral direction toward the exhaust port can also be improved.

  In the invention of claim 4, the blade is not twisted perpendicular to the one-side shroud and the other-side shroud, but is twisted by shifting the portion on the other-side shroud side with respect to the portion on the one-side shroud side in the rotational direction. It is possible to eliminate the generation of eddy currents and wasteful flow by adjusting the distribution of the upper and lower winds in the casing surrounding the same.

  In the invention of claim 5, the blades are not perpendicular to the one-side shroud and the other-side shroud, but are twisted by shifting the other-side shroud-side portion opposite to the rotational direction with respect to the one-side shroud-side portion. The distribution of the upper and lower winds in the casing surrounding the blades can be adjusted to an arbitrary position.

  In the invention of claim 6, the intermediate shroud is disposed without using a special mold structure such as a nesting by forming the outer shape of the intermediate shroud to be substantially the same as the inner shape of the one side shroud or the other side shroud. Therefore, the mold structure for manufacturing the fan can be facilitated.

  According to the first aspect of the present invention, the flow velocity distribution at the exhaust port becomes uniform, which can contribute to noise reduction when the actual machine is incorporated.

  According to the second aspect of the present invention, it is possible to further reduce noise when the actual machine is incorporated.

  According to invention of Claim 3, the flow velocity distribution of the axial direction of an impeller and an outer peripheral direction can be improved.

  According to the invention of claim 4, by adjusting the air flow distribution accompanying the rotation of the blades to be uniform, generation of vortex flow and wasteful flow is eliminated, and noise is maintained while the air volume-static pressure characteristics are substantially equal. Can be reduced.

  According to the fifth aspect of the present invention, it is possible to reduce noise in a state where, for example, a duct or the like is attached by adjusting the distribution of the air flow accompanying the rotation of the blades to an arbitrary position.

  According to the invention of claim 6, the mold structure for manufacturing the fan can be facilitated.

It is a top view of the fan in the 1st example of the present invention. It is a perspective view of an impeller same as the above. It is a principal part sectional drawing of a fan same as the above. It is a principal part sectional drawing of the fan as a modification same as the above. It is a perspective view of the case member as another modification same as the above. It is sectional drawing of the fan which shows 2nd Example of this invention. It is a top view of an impeller same as the above. It is a perspective view of an impeller same as the above. It is a graph which shows the comparison of the air volume-static pressure characteristic of the fan in a prior art example and 2nd Example. It is a perspective view of the impeller as an alternative example same as the above. It is sectional drawing of the fan in a prior art example.

  Hereinafter, preferred embodiments of the fan according to the present invention will be described with reference to the accompanying drawings. In addition, the same code | symbol is attached | subjected to the common structure about each Example, and duplication is demonstrated about a common location as much as possible.

  1 to 5 are each a diagram of a fan showing a first embodiment of the present invention. First, the structure of the fan shown in FIGS. 1 to 3 will be described. 1 is a resin impeller formed in a drum shape, 2 is a flat casing that forms the outer shell of the fan, and the impeller 1 is the casing 2. It is accommodated and held in a rotatable state around the rotation shaft 3 inside. The casing 2 is configured by combining a case member 4 having an upper surface and a side surface and a cover member 5 having a lower surface thereof, and the cover member 5 is mounted so as to cover a lower opening of the case member 4. An intake port 7 is provided on the upper surface of the casing 2 so as to face the upper portion in the axial direction of the impeller 1, and an exhaust port 8 is provided on the side surface of the casing 2 so as to face the outer peripheral side of the impeller 1. It is done. That is, the intake port 7 and the exhaust port 8 are provided around the impeller 1 and open at positions orthogonal to each other.

  The impeller 1 includes a main plate 12 having a cup-shaped boss portion 11 in the center, a plurality of blades 13 having the same shape arranged in the axial direction, that is, perpendicularly to the outer peripheral portion of the main plate 12, and upper ends of the blades 13. A ring-shaped upper shroud 14 to be connected, a plate-shaped first rectifying plate 15 that is located in the middle of the impeller 1 and then the blade 13 in the axial direction, and is formed in a ring shape so as to connect the blades 13; It is configured with. The upper end of the rotating shaft 3 is fitted in the center of the boss portion 11, and the rotating shaft 3 extending perpendicularly toward the lower surface of the casing 2 is supported by a bearing element (not shown) provided on the cover member 5. Is done. Further, a metal rotor frame 17 having a magnetized magnet 16 is fitted to the inner peripheral portion of the boss portion 11, and a stator (fixed) (not shown) is disposed around the rotary shaft 3 so as to face the rotor frame 17. Child) is attached. A lead wire 18 for power feeding is connected to the stator, and the impeller 1 attached to the rotor frame 17 rotates around the rotary shaft 3 by the electromagnetic action between the stator and the magnet 16. ing.

  The main plate 12 of the impeller 1 described above is provided at the tip of the connecting portion 21 and the inclined connecting portion 21 having the outer peripheral side surface of the boss portion 11 as a base end and extending downward from there to the outer peripheral direction of the impeller 1. The upper shroud 22 is provided with lower shrouds 22 arranged on the upper surface thereof at equal intervals. The connecting portion 21 may be a spoke-like portion that partially connects the boss portion 11 and the lower shroud 22 as shown in FIG. 1, or the boss portion as shown in FIGS. 2 and 3. It may be a funnel-shaped connection between 11 and the lower shroud 22 without a gap. In the case shown in FIG. 1, since the opening 23 is formed between the plurality of connecting portions 21, an air inlet (not shown) is also provided in the case member 4 so as to face the opening 23, and the casing 2 passes through the opening 23. It is good also as a structure which takes in air to the impeller 1 from the lower side. In any case, the blade 13 is provided on the outer periphery of the impeller 1 with a space from the boss portion 11 so as to surround the outer peripheral side surface of the boss portion 11.

  The plate-like upper shroud 14 and lower shroud 22 are horizontally disposed at the upper end and the lower end of the blade 13 so as to be orthogonal to the rotation axis 3. The first rectifying plate 15 is disposed so as to cross each blade 13 between the upper shroud 14 and the lower shroud 22, and is different from the upper shroud 14 and the lower shroud 22 disposed horizontally, Inclined downward toward the outer periphery of the impeller 1.

  Next, the operation of the motor in the above configuration will be described. When a stator winding (not shown) is energized through the lead wire 18, a rotational force is generated in the impeller 1 attached to the rotor frame 17 by electromagnetic action with the magnet 16, and air entering from the air inlet 7 of the casing 2. Is changed from the direction along the rotary shaft 3 to the outer peripheral direction of the impeller 1 by the centrifugal force of the impeller 1, passes between the blades 13, and is sent out from the exhaust port 8 of the casing 2.

  The flow of air inside the casing 2 at this time will be described in more detail. The air taken into the casing 2 from the air inlet 7 as the impeller 1 rotates is protruded toward the air inlet 7. In order to avoid this, the air enters from the air intake port 25 of the impeller 1 formed between the outer peripheral side surface of the boss portion 11 and the blade 13 downward along the rotary shaft 3. The air that has entered the air intake 25 flows while the direction of the flow gradually changes in the outer peripheral direction of the impeller 1 due to the centrifugal force of the impeller 1, but part of the flow is adjacent to the air intake 25. When passing between the blades 13, the first rectifying plate 15 is guided to the upper side of the blade 13 without going to the lower side of the blade 13, and passes through the hollow casing 2 from the outer peripheral end of the impeller 1. It is sent out to the exhaust port 8 (see the air flow S1 in FIG. 3). On the other hand, the other air that has entered the air intake port 25 is guided to the lower side of the blade 13 by the first rectifying plate 15 without going to the upper side of the blade 13, and similarly in the casing 2 from the outer peripheral end of the impeller 1. It is sent out to the exhaust port 8 (see air flow S2 in FIG. 3).

  In this way, a part of the wind entering from the upper side of the impeller 1 is also guided to the upper side of the blades 13 while the first rectifying plate 15 is provided in the middle portion in the axial direction of each blade 13. Thus, the air taken in from the intake port 7 can be uniformly distributed without being locally biased in the exhaust port 8. Moreover, since the 1st baffle plate 15 is provided so that it may become downward toward the outer periphery of the impeller 1 rather than horizontally, it divides | segments into the upper side and the lower side of the blade | wing 13 from the air intake port 25, respectively. The wind flows while being smoothly guided along the first rectifying plate 15 without significantly impinging on the first rectifying plate 15 in the middle.

In the experiment, by providing the first rectifying plate 15 having such a structure, a noise improvement effect of about 2 dB (7%) was recognized in the low-frequency rotation region, and the actual load region (wind speed: 0.22 m ³ / (min, static pressure), a noise improvement effect of about 1 dB (43 dB → 42 dB) was observed.

  FIG. 4 is a cross-sectional view of the main part of a fan as a preferred modification of the above embodiment. In this figure, here, assuming that the height to the upper end along the axial direction of the boss portion 11 is h1, and the height to the upper end of each blade 13 is h2, with the lower end of the blade 13 as a reference, The height is 2/3 or less of the height of the blade 13. Other configurations are the same as those of the fan shown in FIGS.

  Also in this example, the air taken into the casing 2 from the air inlet 7 with the rotation of the impeller 1 avoids the boss portion 11 protruding toward the air inlet 7 so that the outer periphery of the boss portion 11 is avoided. The air enters from the air intake 25 of the impeller 1 formed between the side surface and the blade 13 downward along the rotary shaft 3. At that time, by suppressing the height h1 of the boss portion 11 to 2/3 or less of the height h2 of the blade 13, the resistance of the boss portion 11 against the flow of wind from the inlet 7 to the blade 13 is reduced. The large air intake port 25 can be formed by the blade portion 1, and the noise when the fan is incorporated into the actual machine can be further reduced. Since the subsequent air flow is as described in the embodiment of FIGS.

In the experiment, by using the boss portion 11 having a structure as shown in FIG. 4, a noise improvement effect of about 3 dB (7%) is recognized in the low frequency range, and the actual load range (wind speed: 0.22 m ³ / (min, static pressure), a noise improvement effect of about 2 dB (43 dB → 41 dB) was observed.

  FIG. 5 is a perspective view seen from the lower opening side of the case member 4 which is a further preferred modification of the above embodiment. In the figure, a thin plate-like second rectifying plate 29 is provided on the inner side surface of the case member 4 so as to face the vicinity of the exhaust port 8. The second rectifying plate 29 is formed integrally with the case member 4 and substantially vertically along the rotation shaft 3 so as not to receive the resistance of the wind from the impeller 1 toward the exhaust port 8 as much as possible. Here, the second rectifying plate 29 is provided on the case member 4, but instead or in addition, the cover member 5 may be provided. In short, one or a plurality of members may be provided on the member constituting the casing 2. . About another structure, it is common with each example of the said FIGS. 1-4.

  As described above, the air sent from the upper side of the blade 13 and the air sent from the lower side of the blade 13 across the first rectifying plate 15 are sent to the exhaust port 8 through the inside of the casing 2. All the air from the outer peripheral end of the impeller 1 is adjusted to flow toward the exhaust port 8 by the second rectifying plate 29. Therefore, the flow velocity distribution in the axial direction of the impeller 1 can be further improved as compared with the above examples, and the flow velocity distribution in the outer peripheral direction toward the exhaust port 8 can be improved. The other air flows are the same as those described in the examples of FIGS.

  As described above, the fan of this embodiment includes the impeller 1 and the casing 2 provided with the intake port 7 in the axial direction of the impeller 1 and provided with the exhaust port 8 in the outer peripheral direction of the impeller 1. The first rectifying plate 15 is arranged in the middle portion of the impeller 1 in the axial direction, and the first rectifying plate 15 is provided downward toward the outer periphery of the impeller 1.

  In this way, a part of the wind sucked from the intake port 7 with the rotation of the impeller 1 can be guided to the exhaust port 8 from the upper side toward the intake port 7 of the impeller 1 by the first rectifying plate 15. The remaining wind is guided to the lower side opposite to the intake port 7 of the impeller 1 with the first rectifying plate 15 interposed therebetween, and can be guided to the exhaust port 8 without significantly impeding the flow of the wind. it can. As a result, it is possible to appropriately adjust the flow of wind on the upper side, which is one side of the first rectifying plate 15, and the lower side, which is the other side, to make the flow velocity distribution at the exhaust port 8 uniform. This can contribute to noise reduction when the fan is incorporated into an actual machine.

  Moreover, in the modification of a present Example, the impeller 1 arrange | positions the several blade | wing 13 around the boss | hub part 11, and the height h1 of the boss | hub part 11 becomes 2/3 or less of the height h2 of the blade | wing 13. It is formed as follows.

  Thus, if the height h1 of the boss portion 11 is suppressed to 2/3 or less of the height h2 of the blade 13, the resistance of the boss portion 11 against the flow of air from the inlet port 7 to the blade 13 can be reduced. Noise during installation can be further reduced.

  Furthermore, in another modification of the present embodiment, a second rectifying plate 29 is provided inside the casing 2. Thus, by providing another second rectifying plate 29 also inside the casing 2, the flow velocity distribution in the axial direction of the impeller 1 can be improved, and the flow velocity distribution in the outer peripheral direction toward the exhaust port 8 can also be improved.

  6 to 10 are views of the fan showing the second embodiment of the present invention. The differences between the fan configuration shown in FIGS. 6 to 8 and the first embodiment will be described. The casing 2 is configured by combining the case member 4 and the cover member 5 as in the first embodiment. However, the case member 4 here forms the side surface and the lower surface of the casing 2, and the cover member 5 forms the upper surface of the casing 2. A cylindrical sleeve 31 that protrudes upward toward the cover member 5 is integrally formed at the center of the case member 4, and a bearing element 32 that supports the rotary shaft 3 is fitted into the sleeve 31. The Of course, instead of that, the casing 2 may be configured as shown in the first embodiment, and conversely, the configuration of the casing 2 including the sleeve 31 and the bearing element 32 shown in the present embodiment is changed to the first embodiment. You may apply to an Example.

  A stator 33 is mounted on the outer periphery of the sleeve 31 so as to be covered with the boss portion 11 around the rotary shaft 3. Due to the electromagnetic action of the stator 31 and the magnet 16, the impeller 1 attached to the rotor frame 17 rotates about the rotation shaft 3 in the direction of arrow R (counterclockwise as viewed from the top surface of the impeller 1). It has become.

  Although the impeller 1 is configured by disposing the blade 13 between the ring-shaped upper shroud 14 and the lower shroud 22, a ring-shaped intermediate shroud 34 is provided instead of the first rectifying plate 15. The intermediate shroud 34 and the outer peripheral side surface of the boss portion 11 are connected by a plurality of spoke-like connecting portions 21. The connecting portion 21 is located at an intermediate portion in the axial direction of the impeller 1 and extends horizontally in all directions from the outer peripheral side surface of the boss portion 11 toward the intermediate shroud 34, and the main plate 12 of the impeller 1 has a boss portion 11. , The connecting portion 21 and the intermediate shroud 34. Further, an opening 33 is formed between the boss portion 11 and the intermediate shroud 34 at a portion excluding the connecting portion 21. The impeller 1 of the present embodiment is provided with air intake ports 25 and 35 at the upper and lower portions thereof, so that the intake air that guides air to the air intake port 25 facing not only the upper surface but also the lower surface of the casing 2. Ports 7 and 37 are provided. In addition, it does not ask | require about the shape of the spoke in the connection part 21. FIG.

  As shown in FIG. 8, in the impeller 1 of the present embodiment, the portion 13B connected to the lower shroud 22 is shifted in the rotation direction of the arrow R with respect to the portion 13A connected to the upper shroud 14 of each blade 13. It is characterized in that it is arranged and all the blades 13 are twisted. That is, each blade 13 is not perpendicular to the upper shroud 14 or the lower shroud 22 along the direction of the rotation axis 3, but the portion 13 </ b> B connected to the lower shroud 22 has an arrow rather than the portion 13 </ b> A connected to the upper shroud 14. It is arranged so as to be inclined with respect to the direction of the rotation axis 3 so as to be directed in the rotation direction of R. Here, the flat blades 13 formed only by a flat surface having no curved surface are arranged in a state of being twisted around the boss portion 11, or at least a surface facing the rotation direction or a surface opposite to the rotation direction. The twisted plate-like blades 13 formed on the curved surface may be arranged in a state of being further twisted around the boss portion 11. In short, the air flow S (see FIG. 6) in the casing 2 is smoothly made. Each blade 13 may be twisted so that the flow direction is not locally biased.

  As shown in FIG. 6, the impeller 1 of the present embodiment has an intermediate shroud 33 disposed between the upper shroud 14 and the lower shroud 22, and a mold structure for molding these parts. Therefore, the inner diameter of the lower shroud 22 is substantially the same as the outer diameter of the upper shroud 14, and the inner diameter of the upper shroud 14 is substantially the same as the outer diameter of the intermediate shroud 33. Preferably, the inner diameter of the lower shroud 22 is slightly larger than the outer diameter of the upper shroud 14 so that the movable type (not shown) that moves in the direction of the rotating shaft 3 can be opened and closed without hindrance. Is formed to be slightly larger than the outer peripheral diameter of the intermediate shroud 33.

  As a modification, the inner diameter of the upper shroud 14 is substantially the same as the outer diameter of the lower shroud 22 (preferably slightly larger than the outer diameter of the lower shroud 22), and the inner diameter of the lower shroud 22 is The intermediate shroud 33 may be formed to have substantially the same outer diameter (preferably slightly larger than the outer diameter of the intermediate shroud 33). The upper shroud 14, the lower shroud 22, and the intermediate shroud 33 may not be ring-shaped as in this embodiment, but the outer shape of the intermediate shroud 33 is substantially the same as the inner shape of the upper shroud 14 or the lower shroud 22. Thus, the intermediate shroud 33 can be formed integrally with the upper shroud 14 or the lower shroud 33 with a simple mold structure without requiring a special mold structure such as a nest. Since the other configuration is the same as that of the first embodiment, the description thereof is omitted here.

  Next, the operation of the motor in the above configuration will be described. When the winding of the stator 33 is energized via the lead wire 18, a rotational force is generated in the impeller 1 attached to the rotor frame 17 by the electromagnetic action with the magnet 16, and the blades are blown from the intake ports 7 and 37 of the casing 2. The flow of air entering the air intake ports 25 and 35 of the car 1 is converted from the direction along the rotary shaft 3 to the outer peripheral direction of the impeller 1 by the centrifugal force of the impeller 1 and passes between the blades 13. Then, the air is sent out from the exhaust port 8 of the casing 2 provided in the direction orthogonal to the intake ports 7 and 37.

  FIG. 6 shows the air flow S in the casing 2 at this time in the direction of the arrow. The air from the air intake ports 25 and 35 of the impeller 1 toward the outer peripheral blades 13 passes between the blades 13 while being rectified by the intermediate shroud 33 to the upper and lower portions of the blades 13. At this time, in the rotation direction of the impeller 1, the blade 13 reaches the portion 13 </ b> B connected to the lower shroud 22 earlier than the portion 13 </ b> A connected to the upper shroud 14. 2 are all guided to the air intake 25 of the impeller 1 without being guided to the upper surface side, and the occurrence of the offset vortex S ′ (see FIG. 11) as in the conventional example can be prevented. And since it can adjust so that the distribution of the up-and-down wind in the casing 2 surrounding the blade | wing 13 may be equalized, generation | occurrence | production of the offset eddy current S 'and the useless flow to the upper surface side in the casing 2 can be eliminated. it can.

  FIG. 9 compares the air volume-static pressure characteristics in the conventional example and this example. In the figure, the relationship between the air volume and the static pressure is almost the same between the conventional example and this example in any region, but at the same static pressure (= 0 Pa), the noise level of the fan of the conventional example is 37.5 dBA. On the other hand, the noise level of the fan in this embodiment is reduced and improved to 36.4 dBA. That is, in the fan of the present embodiment, the blades 13 are intentionally twisted instead of along the rotation shaft 3 so that the air sucked from the intake ports 7 and 37 of the casing 2 can be smoothly and smoothly distributed. It is possible to reduce the noise with the same air volume-static pressure characteristics by guiding to the air intake ports 25 and 35 of the impeller 1.

  FIG. 10 is a perspective view of an impeller 1 as an alternative example of the above embodiment. Here, the impeller 1 is arranged such that the portion 13B connected to the lower shroud 22 is shifted in the opposite direction of the rotation direction of the arrow R with respect to the portion 13A connected to the upper shroud 14 of each blade 13. 13 is characterized by twisting 13. That is, each blade 13 is not perpendicular to the upper shroud 14 or the lower shroud 22 along the direction of the rotation axis 3, but the portion 13 </ b> A connected to the upper shroud 14 is an arrow rather than the portion 13 </ b> B connected to the lower shroud 22. It is arranged so as to be inclined with respect to the direction of the rotation axis 3 so as to be directed in the rotation direction of R. Also in this case, each flat blade 13 formed only by a flat surface having no curved surface is arranged in a state of being twisted around the boss portion 11, or at least a surface facing the rotation direction or a surface opposite to the rotation direction. Alternatively, the twisted plate-like blades 13 having a curved surface may be arranged around the boss portion 11 in a further twisted state. Since it has the same structure as the fan shown to the said FIGS. 6-8 except the said blade | wing 13, description is abbreviate | omitted.

  When a rotational force is generated in the impeller 1 in the same manner as in the above embodiment, the flow of air entering the air intake ports 25 and 35 of the impeller 1 from the intake ports 7 and 37 of the casing 2 is the centrifugal force of the impeller 1. The direction is changed from the direction along the rotating shaft 3 to the outer peripheral direction of the impeller 1 by force, and is sent from the exhaust port 8 of the casing 2 that passes between the blades 13 and is orthogonal to the intake ports 7 and 37. Is done.

  Here, air from the air intake ports 25 and 35 of the impeller 1 toward the outer peripheral blades 13 passes between the blades 13 while being rectified by the intermediate shroud 33 to the upper and lower portions of the blades 13. In the rotational direction of the vehicle 1, since the portion 13 </ b> A connected to the upper shroud 14 reaches the blade 13 earlier than the portion 13 </ b> B connected to the lower shroud 22, the air intake ports 25, 35 are connected to the intake holes 7, 37. The amount of air introduced to each can be adjusted appropriately. And it becomes possible to aim at reduction of a noise in the state which attached the duct etc. to the fan by adjusting the distribution of the wind in the casing 2 surrounding the blade | wing 13 to arbitrary positions.

  As described above, the fan of the present embodiment is a fan in which a plurality of blades 13 are arranged between the upper shroud 14 that is one side shroud and the lower shroud 22 that is the other side shroud. On the other hand, the portion 13B on the lower shroud 22 side is shifted in the rotation direction indicated by the arrow R, and the blades 13 are arranged in the circumferential direction of the impeller 1.

  In this way, the blade 13 is not perpendicular to the upper shroud 14 and the lower shroud 22, but the portion 13B on the lower shroud 22 side with respect to the portion 13A on the upper shroud 14 side is rotated in the direction indicated by the arrow R. By twisting and twisting, the distribution of the upper and lower winds in the casing 2 surrounding the blades 13 is adjusted to be uniform to eliminate the generation of eddy currents and wasteful flow, and the air volume-static pressure characteristics remain substantially equal. Noise can be reduced.

  As an alternative, the lower shroud 22 side portion 13B is shifted from the upper shroud 14 side portion 13B in the direction opposite to the rotation direction indicated by the arrow R, and the blades 13 are arranged in the circumferential direction of the impeller 1. You may arrange.

  Also in this case, the blade 13 is not perpendicular to the upper shroud 14 and the lower shroud 22, but the portion 13B on the lower shroud 22 side with respect to the portion 13A on the upper shroud 14 side in the rotational direction indicated by the arrow R. By twisting in the opposite direction, the distribution of the upper and lower winds in the casing 2 surrounding the blades 13 can be adjusted to an arbitrary position, and for example, noise can be reduced with a duct or the like attached. Become.

  Further, in this embodiment, an intermediate shroud 33 is disposed between the upper shroud 14 and the lower shroud 22, and the outer shape of the intermediate shroud 33 is formed substantially the same as the inner shape of the upper shroud 14 or the lower shroud 22. is doing.

  In this way, by forming the outer shape of the intermediate shroud 33 substantially the same as the inner shape of the upper shroud 14 or the lower shroud 22, the intermediate shroud 33 can be disposed without using a special mold structure such as a nest. The mold structure for manufacturing the fan can be facilitated.

  In addition, this invention is not limited to said each Example, A various deformation | transformation implementation is possible. For example, instead of providing the first rectifying plate 15 over the entire circumference of the impeller 1, the first rectifying plate 15 may be provided at intervals in the circumferential direction. Further, a fan in which the features of the respective parts of the first and second embodiments are appropriately combined, such as incorporating the features of the boss portion 11 shown in FIG. 4 into the second embodiment, may be configured.

DESCRIPTION OF SYMBOLS 1 Impeller 7 Intake port 8 Exhaust port 11 Boss part 13 Blade 14 Upper shroud (one side shroud)
15 First current plate 22 Lower shroud (other shroud)
29 Second rectifying plate 33 Intermediate shroud

Claims (6)

Impeller,
A casing provided with an intake port in the axial direction of the impeller and an exhaust port provided in the outer peripheral direction of the impeller;
A first baffle plate in the middle in the axial direction of the impeller;
The fan, wherein the first current plate is provided downward toward the outer periphery of the impeller.   The fan according to claim 1, wherein the impeller includes a plurality of blades arranged around a boss portion, and the height of the boss portion is 2/3 or less of the height of the blade.   The fan according to claim 1 or 2, wherein a second baffle plate is provided inside the casing. In a fan in which blades are arranged between one side shroud and the other side shroud,
The fan is characterized in that the blades are arranged by shifting the portion on the other shroud side in the rotational direction with respect to the portion on the one side shroud side. In a fan in which blades are arranged between one side shroud and the other side shroud,
The fan is characterized in that the blades are arranged by shifting the portion on the other shroud side opposite to the portion on the one side shroud side in the direction opposite to the rotation direction. An intermediate shroud is disposed between the one side shroud and the other side shroud;
The fan according to claim 4 or 5, wherein an outer shape of the intermediate shroud is formed to be substantially the same as an inner shape of the one-side shroud or the other-side shroud.

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