JP5907205B2 - Blower - Google Patents

Description

  The present invention relates to a blower device having a rotating impeller.

  Conventionally, high-density mounting has been performed in a casing of a thin device such as a notebook computer or a liquid crystal projector, and the installation space of a blower for cooling a heat-generating component has been limited. Therefore, a method of using a centrifugal fan as shown in Patent Documents 1 and 2 as a blower and taking in air from a direction perpendicular to the blowing direction of the impeller and exhausting toward the blowing direction of the impeller has become mainstream. .

JP-A-11-141499 JP 2008-255865 A

  However, the conventional blower has the following problems.

  The above centrifugal fan has the same shape on one side and the other side in the intake direction. Therefore, although the performance of the blower unit alone (free air) is good, the static pressure is low and sufficient performance cannot be exhibited when incorporated in a thin device. In particular, in thin equipment, the intake space is restricted due to restrictions on various parts, and a high static pressure blower is required inside a dense housing. However, it is difficult to mount a large blower inside the housing to be miniaturized, and the blower itself is required to be thin and small.

  Further, as the amount of heat generated by the heat-generating component increases, a higher air volume is required as a blower, and in recent years, there has been a strong demand for noise reduction. On the other hand, thinning of thin devices has further progressed, and even the air intake space of the blower cannot be secured sufficiently. As a result, the performance as a blower device is remarkably deteriorated, and countermeasures against heat of thin devices are a major issue, and the performance of the blower device is insufficient with respect to the amount of heat generated.

  Therefore, in view of the above problems, the present invention has an object to provide a blower device that exerts maximum performance when a thin device is incorporated and that can achieve noise reduction by modifying the shape of the impeller. .

According to the first aspect of the present invention, by appropriately setting the ratio of the inner diameter to the outer diameter of the blade, noise is not noticeable when the impeller rotates, and a sufficient air volume can be obtained. Noise reduction can be realized. Further, the cross-sectional area of ventilation between adjacent blades can be increased, the efficiency of intake and exhaust can be improved, the air volume can be further increased, and the noise at the same air volume can be further reduced. In addition, air can be smoothly passed between the tips of adjacent blades, exhaust efficiency from the impeller can be improved, and the air volume can be increased. In addition, by appropriately setting the ratio of the outer diameter of the disc to the inner diameter of the blade, it is possible to improve the efficiency of intake and exhaust as a blower, further increase the air volume, and reduce the noise at the same air volume. Further reduction can be achieved. In addition, the intake portion of the casing is formed in the suction direction of the impeller so that the inner peripheral end of the blade faces the intake portion, while the outer peripheral end of the blade faces the exhaust portion. Exhaust efficiency can be increased by extending to the outside.

  In the invention of claim 2, by appropriately setting the mounting angle of the blade, air flows smoothly along the blade, and the centrifugal force of the blade accompanying the rotation of the impeller appropriately acts, and is the same as the blower Noise reduction at the time of air volume can be realized.

  In the invention of claim 3, by setting the number of blades disposed on the impeller to be 35 or more, the air flow toward the discharge direction of the impeller can be made uniform, and noise at the same air volume can be further reduced.

In the invention of claim 4 , intake is performed satisfactorily by opening the intake portions on both sides in the suction direction of the impeller.

According to the invention of claim 1, by adding a device to the shape of the impeller, it is possible to provide a blower device that exhibits the maximum performance when a thin device is incorporated and can realize noise reduction. Further, the efficiency of intake and exhaust can be improved, the air volume can be further increased, and noise at the same air volume can be further reduced. Further, the exhaust efficiency from the impeller can be improved. Furthermore, exhaust efficiency can be increased.

  According to the invention of claim 2, by adding a device to the shape of the impeller, it is possible to provide a blower device that exhibits the maximum performance at the time of incorporation of a thin device and can realize noise reduction.

  According to the invention of claim 3, noise at the same air volume can be further reduced.

According to the invention of claim 4, intake is performed satisfactorily.

It is a longitudinal cross-sectional view of the air blower which shows the 1st reference example of this invention. It is a top view of an impeller same as the above. It is a top view of the state which removed the cover of the air blower which shows 1st Example of this invention. It is a longitudinal cross-sectional view of the state which removed the cover of the air blower same as the above. It is a top view of the state which mounted | wore with the cover of the air blower as a modification same as the above. It is a longitudinal cross-sectional view of the state which mounted the cover of the ventilation apparatus as a modification same as the above. It is a top view of the air blower which shows the 2nd reference example of this invention. It is a bottom view of an air blower same as the above. It is a side view of an air blower same as the above. It is a longitudinal cross-sectional view of an air blower same as the above. It is a top view of the whole impeller same as the above. It is a principal part enlarged plan view of an impeller same as the above. It is a principal part enlarged plan view of an impeller same as the above.

Hereinafter, preferred embodiments and reference examples of a blower according to the present invention will be described with reference to the accompanying drawings. In actual施例and Reference Examples are shown in the following, reference numeral common to each common point, a description of the common parts as much as possible to avoid duplication omitted.

Reference example 1

FIG. 1 shows an example in which the blower in the first reference example of the present invention is applied to a thin electronic device such as a notebook computer. In the figure, a fan motor 1 as a blower has a flat outer shape as a whole and is accommodated in a thin electronic device. The fan motor 1 includes a fan 2 as a blower. The casing 3 that forms the outline of the fan motor 1 is constituted by, for example, a bottomed case member 4 made of a member having excellent heat conductivity and a cover 5 that covers the upper opening of the case member 4. In order to reduce the thickness, the casing 3 itself may be formed as a part of the casing of the thin electronic device.

  The fan 2 includes a bottomed cylindrical sleeve 7 that is fixed upright to the case member 4, a stator 8 that is provided on the outer periphery of the sleeve 7, and that has a stratified iron core on which windings are mounted. A substrate 9 that is electrically connected to the end of the wire and on which one or a plurality of electronic components (not shown) are mounted to form a motor drive circuit, and a rotor 10 that rotates by receiving magnetic force from the stator 8 And is configured. A cylindrical bearing 11 is inserted into the sleeve 7, and one end of a shaft 12 as a rotating shaft that is rotatably supported in the sleeve 4 by the bearing 11 is at the center of the rotor 10. Installation fixed.

  The rotor 10 is provided with a metal yoke 15 disposed so as to surround the stator 8, a permanent magnet 16 provided on the inner peripheral surface of the yoke 15, and an outer peripheral surface of the yoke 15, and a plurality of blades 17. , 18, 18, and 18, 18 by applying a predetermined current to the windings of the stator 8 through the substrate 9, thereby attracting the permanent magnet 16 facing the stator 8. In addition, a repulsive force is generated, and the rotor 10 rotates about the shaft 12.

In the casing 3, intake ports 21 and 22 are formed as intake portions on both sides in the axial direction of the rotor 10, which is also the suction direction of the impeller 19. In the present reference example, the intake ports 21 and 22 are provided in the case member 4 and the cover 5 constituting the casing 3, respectively. However, for example, only one intake port 21 may be provided. Although not shown, an exhaust port as an exhaust portion is formed in the radial direction of the rotor 10, which is also the discharge direction of the impeller 19, perpendicular to the intake ports 21 and 22, and the fan motor 1 is a centrifugal fan. It has the configuration as. The number of exhaust ports arranged is not particularly limited.

Next, the configuration of the impeller 19 which is a feature of this reference example will be described in more detail with reference to FIG. The impeller 19 that rotates together with the rotor 10 is configured by arranging the plurality of blades 17 and 18 described above radially on the outer peripheral surface of the fan cup 24 around the shaft 12. A fan cup 24 having a cup shape as a whole extends in a direction away from the air inlet 21 along the axial direction of the rotor 10 from the outer peripheral end surface of the base 25 closed on the side facing the air inlet 21. One end of the shaft 12 is fitted and fixed to a fitting portion 27 provided at the inner center of the base portion 25. An inner surface of the cylindrical portion 26 is formed as a mounting portion for the yoke 15, while a ring-shaped disk 28 is formed on the outer surface of the cylindrical portion 26.

The blade 17 is formed in an arc shape toward the rotation direction R, and the inner peripheral end 17A close to the shaft 12 extends partway through the base portion 25 of the fan cup 24. A recess 31 is formed that is surrounded by the inner peripheral end 17 </ b> A of each blade 17 and receives air from the air inlet 21. In addition, the inner peripheral ends 17A of the blades 17 are not connected to each other, and between the adjacent inner peripheral ends 17A, there are flow guide grooves 32 that uniformly guide the air reaching the recesses 31 toward the outer peripheral side of the blades 17. It is formed. Thus, in this reference example, when the base 25 of the fan cup 24 is viewed from the front, the shape as the blade 17 is formed up to the center of the fan cup 24.

  On the other hand, the outer peripheral end 17B of the blade 17 away from the shaft 12 faces the exhaust port (not shown) as well as the cylindrical portion 26 of the fan cup 24 and extends to the outside of the intake ports 21 and 22. The gap between the adjacent outer peripheral ends 17B of the blades 17 is formed wider than the gap between the inner peripheral ends 17A of the same blades 17, and the air guided between the adjacent blades 17 from the flow guide grooves 32. Is smoothly sent toward the exhaust port by the rotational force of the impeller 19.

Further, in this reference example, another blade 18 having a different shape from the blade 17 is arranged at an equal interval between the adjacent blades 17. The inner peripheral end 18A of the blade 18 is connected to the cylindrical portion 26 of the fan cup 24, and the outer peripheral end 18B of the blade 18 faces an exhaust port (not shown), like the outer peripheral end 17B of the blade 17, and the intake port 21. , 22 extends outward. The blade 18 is also formed in an arc shape like the blade 17, and by arranging the blades 17 and 18 alternately, the flow of air flowing between the blades 17 is made uniform, and the noise as the fan motor 1 is reduced. Is possible.

  In the fan motor 1 having such a configuration, a predetermined current is supplied to the windings of the stator 8 via the substrate 9, and rotational driving force is applied from the stator 8 to the permanent magnet 16 attached to the rotor 10. When given, the rotor 10 including the impeller 19 starts to rotate in the rotation direction R around the shaft 12. At this time, air that has taken heat from a heat-generating component (not shown) inside the thin electronic device is sucked into the blades 17 and 18 from one side of the impeller 19 through one intake port 21, Similar air is also drawn into the blades 17 and 18 from the other side of the impeller 19 from the other intake port 22.

  Here, the inner peripheral end 17 </ b> A of the blade 17 is opposed to the air inlet 21 and extends partway through the base 25 of the fan cup 24, and the air sucked from the air inlet 21 toward the base 25 of the fan cup 24. The centrifugal force accompanying the rotation of the impeller 19 acts and does not stay there, but is guided equally and efficiently from the recess 31 to the flow guide groove 32 formed between the inner peripheral ends 17A of the blades 17. And between each braid | blade 17, air is smoothly sent out from the inner peripheral side of the impeller 19 to the outer peripheral side, and is further rectified by another blade 18 on the way, and from the exhaust port of the casing 3 to the thin electronic device. Exhaust outside with high static pressure and high air volume. That is, as shown in FIG. 1, with the downsizing of thin electronic devices, even when the height shape of the fan motor 1 itself has to be increased, the upper surface of the base portion 25 of the fan cup 24 facing the air inlet 21 is formed. By forming the blade 17 to the extent, the fan motor 1 capable of increasing the static pressure and obtaining a high air volume can be realized according to the conditions of the actual machine.

As described above, in the present reference example, the casing 3 has the intake ports 21 and 22 as one or more intake portions and the exhaust ports as one or more exhaust portions, and rotates to the central portion in the casing 3. In the fan motor 1 having a centrifugal fan structure provided with an impeller 19, the impeller 19 is configured by extending a blade 17 from a cylindrical portion 26 forming a side portion of the fan cup 24 to a central portion.

In this case, with the rotation of the impeller 19, air is efficiently led to the blade 17 extending from one air inlet 21 to the center of the fan cup 24. The fan motor 1 with higher static pressure and higher air volume can be provided in accordance with the conditions of the actual machine. Therefore, according to the fan motor 1 of this reference example, the maximum performance can be exhibited when a thin electronic device is incorporated by devising the shape of the impeller 19.

FIGS. 3-6 has shown the fan motor 1 as a ventilation apparatus in 1st Example of this invention. Also in this embodiment, the feature is the shape of the impeller 19, and the other configuration is also described in the first reference example, so that description of common parts is omitted as much as possible.

  The fan motor 1 shown in FIGS. 3 and 4 shows a state in which a cover (not shown) of the casing 3 is removed, but an intake port is provided only in this cover, and an intake air is provided on the bottom surface of the case member 4. It has a configuration without a mouth. Again, the rotor 10 is provided on a metal yoke 15 disposed so as to surround the stator 8, a permanent magnet 16 provided on the inner peripheral surface of the yoke 15, and an outer peripheral surface of the yoke 15. It is composed of a resin impeller 19 having a blade 37, and applies a predetermined current to the winding of the stator 8 through the substrate 9, so that an attractive force is generated between the permanent magnet 16 facing the stator 8. In addition, a repulsive force is generated, and the rotor 10 rotates about the shaft 12.

  Reference numeral 39 denotes an exhaust port serving as an exhaust portion of the casing 3 provided in the discharge direction of the impeller 19. There may be any number of the exhaust ports 39. As a result, when the rotor 10 including the impeller 19 rotates, air is sucked in from the intake port (not shown) in the suction direction of the impeller 19, and the flow direction is changed by the centrifugal force of the rotor 10 to be orthogonal to the intake port. The air flows from the exhaust port 39 of the casing 3 to be operated. This series of air flows is indicated by an arrow F.

The impeller 19 in the present embodiment, the is constituted by a blade 3 7 and the fan cup 24, the fan cup 24 is similar to the first reference example, a base portion 25, a cylindrical portion 26, a fitting portion 27, Each disk 28 is provided. The blades 37 here are of one type, all have the same arc shape, and there are 35 or more. The fan cup 24 is configured by being radially arranged at equal intervals around the shaft 12 on a disk 28 extending in a flange shape from the outer surface of the cylindrical portion 26 of the fan cup 24. Each blade 37 is connected to the disk 28 of the fan cup 24, but is not connected to the cylindrical portion 26 of the fan cup 24, and is between the inner peripheral end 37 A of the blade 37 and the outer surface of the cylindrical portion 26. A gap 40 is formed. Further, the inner peripheral ends 37 </ b> A of the blades 37 are not connected to each other, and the air reaching the gap 40 from the suction direction of the impeller 19 between the adjacent inner peripheral ends 37 </ b> A is evenly directed toward the outer peripheral side of the blades 37. A diversion groove 32 is formed which leads to

  Further, as shown in FIG. 3, the entire blade 37 is arranged in an annular shape so as to surround the rotation center (shaft 12) of the impeller 19, and first blades 37 connecting the inner peripheral ends 37 </ b> A of the blades 37. A second circle that connects the circle and the outer peripheral ends 37 </ b> B of the blades 37 is arranged concentrically around the shaft 12. Here, when the diameter of the first circle is the inner diameter a of the blade 37 and the diameter of the second circle is the outer diameter b of the blade 37, the ratio (a / b) of the inner diameter a to the outer diameter b of the blade 37 is If it is formed to be 60 to 45%, it is possible to realize a higher air volume than the blades 37 of other ratios at the same noise.

5 and 6 show a modification of the first embodiment. The fan motor 1 shown here has a cover 5 for the casing 3, and the casing 3 is provided on both sides in the suction direction of the impeller 19 as an intake section. The intake ports 21 and 22 are formed as openings. Further, between the adjacent blades 37 of the impeller 19, another blade 38 similar to the blade 18 shown in FIG. 1 is arranged at equal intervals. For other configurations, for example, the position of the exhaust port 39 is different, but is basically the same as that of the fan motor 1 of FIGS.

Although the structure of the impeller 19 is as having demonstrated in FIG.3 and FIG.4, another characteristic is shown here. First, the ratio (a / b) of the inner diameter a to the outer diameter b of the blade 37 is set to 60 to 45% as described above. If this ratio (a / b) exceeds 60%, the distance from the inner peripheral end 37A to the outer peripheral end 37B of each blade 37 becomes extremely short, and a sufficient air volume cannot be obtained when the impeller 19 rotates. . Conversely, when the ratio (a / b) is less than 45%, the distance from the inner peripheral end 37A of each blade 37 to the outer peripheral end 37B becomes extremely long, and noise generated when the impeller 19 rotates is conspicuous. Become. In this example, the air flow F sucked into the impeller 19 does not flow out of the intake ports 21 and 22 in the middle, but is efficiently guided to the exhaust port 39, so that the inner peripheral ends 37 </ b> A of the blades 37. Is opposed to the intake ports 21 and 22, while the outer peripheral end 37 </ b> B of the blade 37 faces the exhaust port 39 and extends to the outside of the intake ports 21 and 22.

  Moreover, if the ratio (c / a) of the outer diameter c of the disk 28 to the inner diameter a of the blade 37 is limited to 108 to 120%, the efficiency of intake and exhaust as the fan motor 1 is improved, and the result The air volume increases and noise at the same air volume is reduced. The reason is that if the ratio (c / a) is less than 108%, the air sucked from the intake ports 21 and 22 is efficiently converted into the discharge direction by the disk 28 when the impeller 19 rotates. Conversely, if the ratio (c / a) exceeds 120%, the disk 28 blocks the air flow when the impeller 19 rotates, and the air volume decreases in any case.

Further, the mounting angle θ of each blade 37 is inclined with respect to the conventional one, and is formed in the range of 25 to 45 °. The mounting angle θ here, a straight line from the rotational center O of the impeller 19 through the inner peripheral edge 37A of the blade 37 as XO, straight along the portion extending out from the inner peripheral end 37 A of the line XO and the blade 37 This means an angle formed with X1, and the straight line X1 is located behind the straight line X0 in the rotational direction R. When the mounting angle θ is less than 25 degrees, air is less likely to flow smoothly along the leading edge of each blade 37 in the rotational direction, and noise increases. On the other hand, when the mounting angle θ exceeds 45 degrees, the impeller The centrifugal force due to the blade 37 is less likely to act when the 19 rotates, and it becomes difficult to obtain a sufficient air volume. Therefore, by limiting the mounting angle θ to a range of 25 to 45 °, it is possible to realize a reduction in noise at the same air volume.

  Further, when viewed in the rotational axis direction of the impeller 19 shown in FIG. 5, the thickness d of the blade 37 from the inner peripheral end 37 </ b> A that is the root of the blade 37 to the outer peripheral end 37 b that is the leading end is not uniform and arbitrarily changes. I am letting. Thereby, the ventilation cross-sectional area between the adjacent blades 37 can be increased, the efficiency of intake and exhaust can be improved as the fan motor 1, the air volume can be further increased, and the noise at the same air volume can be further increased. Can be reduced.

  Regarding the thickness d of the blade 37, the thickness t1 around the inner peripheral end 37A, which is the root of the blade 37, is the ratio (t2 / t1) to the thickness t2 around the outer peripheral end 37B, which is the tip of the blade 37. ) Is formed to 60% or less. The reason is that if the ratio (t2 / t1) exceeds 60%, it becomes difficult for air to smoothly pass between the outer peripheral ends 37B of the adjacent blades 37, and the exhaust efficiency from the impeller 19 decreases.

  As described above, in this embodiment, in the fan motor 1 that is a blower device provided with the exhaust port 39 as the exhaust portion of the casing 3 in the discharge direction of the impeller 19, the outer diameter b of the blade 37 provided on the impeller 19. The entire blade 37 is arranged in an annular shape so that the ratio of the inner diameter a to 60 to 45%.

  Thus, by appropriately setting the ratio of the inner diameter a to the outer diameter b of the blade 37, noise is not conspicuous when the impeller rotates, and a sufficient air volume can be obtained. Low noise can be achieved. Therefore, by devising the shape of the impeller 19, the maximum performance can be exhibited and the noise reduction can be realized when a thin electronic device is incorporated.

  In the present embodiment, the blade 37 provided on the impeller 19 is arranged at an attachment angle θ of 25 to 45 ° with respect to a straight line passing from the center of the impeller 19 to the inner peripheral end 37A of the blade 37. .

  Thus, by appropriately setting the mounting angle θ of the blade 37, air flows smoothly along the blade 37, and the centrifugal force of the blade 37 accompanying the rotation of the impeller 19 acts appropriately, and the fan motor 1, it is possible to achieve low noise at the same air volume. Therefore, by devising the shape of the impeller 19, the maximum performance can be exhibited and the noise reduction can be realized when a thin electronic device is incorporated.

  Preferably, the number of blades 37 disposed on the impeller 19 is 35 or more, so that the air flow toward the discharge direction of the impeller 19 can be made uniform, and noise at the same air volume can be further reduced.

  Further, in this embodiment, the thickness d from the inner peripheral end 37A that is the root of the blade 37 to the outer peripheral end 37B that is the tip is arbitrarily changed. As a result, the cross-sectional area of ventilation between the adjacent blades 37 can be increased, and the fan motor 1 can improve the efficiency of intake and exhaust, further increase the air volume, and further increase the noise at the same air volume. Can be reduced.

  More preferably, the ratio (t2 / t1) of the thickness t2 around the outer peripheral end 37B of the blade 37 to the thickness t1 around the inner peripheral end 37A of the blade 37 is 60% or less. Thereby, air can be smoothly passed between the outer peripheral ends 37B of the adjacent blades 37, the exhaust efficiency from the impeller 19 can be improved, and the air volume can be increased.

  The impeller 19 of this embodiment further includes a disk 28 that intersects the blade 17, and the ratio of the outer diameter c of the disk 28 to the inner diameter a of the blade 37 is 108 to 120%.

  Thus, by appropriately setting the ratio of the outer diameter c of the disk 28 to the inner diameter a of the blade 37, the fan motor 1 can improve the efficiency of intake and exhaust, and can further increase the air volume, Further, noise at the same air volume can be further reduced.

Reference example 2

FIGS. 7-13 has shown the fan motor 1 as a ventilation apparatus in the 2nd reference example of this invention. Also in this reference example , the feature is the shape of the impeller 19, and the other configuration is also described in the first reference example, so that description of common parts is omitted as much as possible.

  The rotor 10 is provided with a metal yoke 15 disposed so as to surround the stator 8, a permanent magnet 16 provided on the inner peripheral surface of the yoke 15, and an outer peripheral surface of the yoke 15, and a plurality of blades 47. And by applying a predetermined current to the windings of the stator 8 through the substrate 9, an attractive force and a repulsion between the permanent magnet 16 facing the stator 8 are provided. A force is generated, and the rotor 10 rotates about the shaft 12.

The number and opening positions of the intake ports 21 and 22 and the exhaust ports 39 are not particularly limited as in the other embodiments and reference examples . Also here, when the rotor 10 including the impeller 19 rotates, air is sucked in the suction direction of the impeller 19 from the intake ports 21 and 22 facing each end face of the impeller 19, and the centrifugal force of the rotor 10 causes By changing the flow direction, air flows from the exhaust port 39 of the casing 3 orthogonal to the intake ports 21 and 22. This series of air flows is indicated by an arrow F.

The impeller 19 includes the blade 47 and the fan cup 24. The fan cup 24 includes a base portion 25, a cylindrical portion 26, a fitting portion 27, and a disk 28 as in the first reference example. Each has. However, the disk 28 here is not directly connected to the outer surface of the cylindrical portion 26, but is connected to a plurality of spokes 51 extending from the outer surface of the cylindrical portion 26, so that the cylindrical portion 26 and a ring shape on the outer periphery thereof are connected. A hole 52 that allows air to flow is formed between the disk 28 and the disk 28. The blades 47 are of a single type and all have the same arc shape with the leading edge recessed with respect to the rotational direction R of the impeller 19, and the middle part of each blade 47 crosses the disk 28 and is fixed. . Here too, the blades 47 are configured to be arranged radially at equal intervals around the shaft 12.

  Each blade 47 is connected to the disk 28 of the fan cup 24, but is not connected to the cylindrical portion 26 of the fan cup 24, and is between the inner peripheral end 47 </ b> A of the blade 47 and the outer surface of the cylindrical portion 26. A gap 40 is formed. The inner peripheral ends 47A of the blades 37 are not connected to each other, and the air reaching the gap 40 from the suction direction of the impeller 19 is uniformly guided toward the outer peripheral side of the blades 40 between the adjacent inner peripheral ends 47A. A diversion groove 32 is formed. Each blade 47 is also connected to each other by a ring-shaped connecting body 54 different from the disk 28.

  Further, as shown in FIG. 11, the entire blade 47 is arranged in an annular shape so as to surround the shaft 12 that is the rotation center of the impeller 19, and the first blades that connect the inner peripheral ends 47 </ b> A of the blades 47. A second circle rb that connects the circle ra and the outer peripheral ends 47 </ b> B of the blades 47 is arranged concentrically around the shaft 12.

  Here, paying attention to the outer peripheral end 47B of each blade 47, as shown in FIG. 10 in particular, the intake port 21 is more than the outer diameter b1 of the circle connecting the end surfaces of the outer peripheral end 47B most opposed to the intake ports 21 and 22. , 22 is formed with a large outer diameter b2 of the circle connecting the end faces of the outer peripheral end 47B located in the middle part away from the center. That is, when viewed in the longitudinal cross-sectional shape of the impeller 19, each blade 47 has an outer diameter toward the exhaust port 39 on the outer peripheral side of the impeller 19 rather than the outer diameter b <b> 1 of the outer end surface 47 </ b> B facing the intake ports 21 and 22. It has the convex part 55 which protruded b2, and it becomes possible to make the flow of the air toward the exhaust port 39 uniform, and to increase an air volume by this.

  As shown in FIG. 12, the mounting angle θa on the inner peripheral end 47A side of each blade 47 is larger than the mounting angle θb on the outer peripheral end 47B side of each blade 47, and the mounting angles θa and θb are different angles. Yes. The mounting angle θa extends when the curved surface formed at the front edge on the inner peripheral end 47A side of the blade 47 is extended, and the intersecting points at which the curved surface intersects the first circle ra and the second circle rb are defined as ya and yb, respectively. The angle formed by the straight line Sa connecting the intersections ya and yb and the tangent line Sb of the first circle ra. Further, the attachment angle θb extends when the curved surface formed on the front edge on the outer peripheral end 47B side of the blade 47 is extended, and the intersections of the curved surface intersect with the first circle ra and the second circle rb are defined as za and zb, respectively. The angle formed by the straight line Ta connecting the intersections za and zb and the tangent line Tb of the first circle ra.

  Then, by making the mounting angles θa and θb of the blade 47 different, the direction of the intake side and the exhaust side of the blade 47 can be effectively changed, and the air volume can be increased.

  Further, as shown in FIG. 13, the curvature Ra of the curved surface formed at the front edge on the inner peripheral end 47A side of the blade 47 is different from the curvature Rb of the curved surface formed on the front edge on the outer peripheral end 47B side of the blade 47. Even so, the direction of the intake side and the exhaust side of the blade 47 can be effectively changed, and the air volume can be increased.

As described above, in this reference example , the exhaust port 39 as the exhaust portion of the casing 3 is provided in the discharge direction of the impeller 19, and the fans 21 and 22 as the intake portions are provided at positions perpendicular to the exhaust port 39. In the motor 1, the blade 47 provided on the impeller 19 has a convex portion 55 that protrudes the outer diameter b <b> 2 to the outer peripheral side rather than the outer diameter b <b> 1 of the end surface facing the intake ports 21 and 22.

  In this way, the air sucked into the impeller 19 is guided to the blade 47 rotating to the vicinity of the exhaust port 39 by the convex portion 55 formed on the blade 47, and therefore directed toward the exhaust port 39. It is possible to make the air flow uniform and increase the air volume. Therefore, by adding a device to the shape of the impeller 19, it is possible to provide the fan motor 1 that exhibits the maximum performance when incorporating a thin electronic device.

Further, in the present reference example , the mounting angles θa and θb are different between the inner peripheral side and the outer peripheral side of the blade 47, thereby effectively changing the direction of the intake side and the exhaust side of the blade 47 to increase the air volume. It becomes possible. Therefore, also in this case, by adding a device to the shape of the impeller 19, it is possible to provide the fan motor 1 that exhibits the maximum performance when a thin electronic device is incorporated.

Further, in this reference example , the curvatures Ra and Rb are different between the inner peripheral side and the outer peripheral side of the blade 47, thereby effectively changing the direction of the intake side and the exhaust side of the blade 47 to increase the air volume. Is possible. Therefore, also in this case, by adding a device to the shape of the impeller 19, it is possible to provide the fan motor 1 that exhibits the maximum performance when a thin electronic device is incorporated.

In addition, this invention is not limited to the said Example, A various change is possible in the range which does not deviate from the meaning of this invention. For example, the definition of the mounting angle θ of the blade 37 in the first embodiment and the mounting angles θa and θb of the blade 47 in the second reference example are different, but the point is that the blades 37 and 47 with respect to the center of the impeller 19 are important. Any angle may be used as long as it is an attachment angle, and either definition may be adopted in each embodiment or reference example , and other definitions may have the same purpose.

3 Casing 37 Blade 19 Impeller 21, 22 Air intake (intake part)
24 Fan cup 28 Disc 37A Inner edge
37B Outer peripheral end 39 Exhaust port (exhaust part)

Claims (4)

In the air blower in which the impeller is constituted by a blade and a fan cup, and an exhaust part of the casing is provided in the discharge direction of the impeller.
The fan cup is provided with a disk, the blade is provided on the disk, the blade is not connected to the fan cup, and the ratio of the inner diameter to the outer diameter of the blade is 60 to 45%,
Change the thickness from the base of the blade to the tip arbitrarily,
The ratio of the thickness of the tip to the thickness of the root of the blade is 60% or less,
The ratio of the outer diameter of the disc to the inner diameter of the blade is 108 to 120% ,
Forming the opening of the casing in the suction direction of the impeller,
An air blower characterized in that an inner peripheral end of the blade is opposed to the intake portion, and an outer peripheral end of the blade is extended to the outside of the intake portion so as to face the exhaust portion .   The blower according to claim 1, wherein the blade is disposed at an attachment angle of 25 to 45 ° with respect to a straight line passing through an inner peripheral end of the blade from the center of the impeller.   The blower according to claim 1 or 2, wherein the number of blades is 35 or more. The blower according to any one of claims 1 to 3 , wherein the intake portions are respectively formed to be open on both sides in the suction direction of the impeller .

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