JP5128555B2 - Impeller and fan device - Google Patents

Description

  The present invention relates to an impeller and a fan device that have blades of forward blades and generate an air flow along a central axis direction that is a center of rotation.

  Conventionally, electronic devices such as personal computers or servers have been provided with a cooling fan for cooling the electronic components inside the housing, and the performance of the cooling fan as the installation density of the electronic components inside the housing increases. Improvement is required. Mainly, there are two types of cooling fans: an exhaust fan for exhausting high-temperature air staying inside the housing to the outside of the housing, and a blower fan that directly blows cooling air to the heat generating electronic components Exists. Among these, in the latter blower fan, the flow direction of the blown air flow is important.

  When the cooling air is directly blown to the heat generating electronic component, it is desirable that the flow rate of the air flow directly blown to the electronic component is large, and the latter blower fan is suitable for such an application.

  For the blower fan, an impeller having blades of forward blades is often used. This is because the blade of the forward wing has a characteristic of sending out the air flow while suppressing the outward spread in the radial direction. Here, the forward blade shape refers to, for example, an intersection between the leading edge in the rotational direction of the blade and the radially outer end of the blade and the central axis as in the impeller used in the axial blower described in Patent Document 1. This means that the straight line is located on the front side in the rotational direction from the intersection of the leading edge of the wing and the base of the wing, and there are various degrees of advancement.

  Here, when the impeller rotates, centrifugal force acts on the blade itself. Centrifugal force is generated substantially parallel to the radial direction when viewed from the root of the blade support. The impeller that rotates at high speed needs to be designed with strength in consideration of the stress generated at the base of the wing by centrifugal force. The effect of such centrifugal force becomes more pronounced as the impeller rotates at a higher speed.

For example, an impeller of the fan apparatus described in Patent Document 1 (hereinafter, referred to as the impeller A) in, for advancing the degree of the wing is greater, the greater the influence of centrifugal force. In the impeller A, since the radially outer end of the blade is positioned far forward in the rotational direction from the root, a large moment is generated at the root of the blade due to the centrifugal force generated at each part of the blade. Therefore, a design that takes moment into consideration is necessary at the base of the wing.

  In addition, there is a concern that the blade is deformed and the radially outer end of the blade is displaced radially outward due to the influence of the centrifugal force described above. If the radially outer end of the blade is displaced radially outward, the radially outer end of the blade may come into contact with the inner surface of the outer frame that surrounds the impeller.

  As an effective measure against the influence of this centrifugal force, Patent Documents 2 to 8 disclose a substantially annular connecting member that connects blades.

  In an impeller provided with such a connecting member, the region located on the radially inner side of the blade connecting member has a great influence on the airflow characteristics of the impeller, and is located on the radially outer side of the blade connecting member. The region has a great influence on the surging characteristics and static pressure characteristics of the impeller.

  Further, in the axial fan, a backflow of the air flow is generated in a gap formed between the inner peripheral surface of the outer frame body that houses the impeller and the radially outer end of the blade. This phenomenon appears prominently in the surging region, and the static pressure characteristic is reduced and the noise is increased in the surging region. This problem appears remarkably when the connecting member is provided at the radially outer end of the blade as in the impellers described in Patent Documents 2 and 4-8. The impeller described in Patent Document 3 is a swept wing and has a different configuration from the impeller according to the present invention.

JP 2008-196480 A US Design Patent No. D511824 US Patent Application Publication No. 2008/0056899 US Pat. No. 6,554,574 US Pat. No. 4,684,324 U.S. Pat. No. 4,569,631 U.S. Pat. No. 4,569,632 US Pat. No. 6,241,474

  Therefore, the problem to be solved by the present invention is to provide an impeller and a fan device that can suppress the influence of centrifugal force on the blades, improve the characteristics of the impeller, and stably blow air.

In order to solve the above-mentioned problem, in the invention of claim 1, the impeller is a support part formed around a central axis, and is formed by extending radially outward from an outer surface of the support part. A plurality of blades that generate an air flow in the direction of the central axis by rotating around the central axis together with the support portion, and formed in a circumferential direction along an arbitrary circle centered on the central axis, A substantially annular connecting member that connects the plurality of blades, and each of the plurality of blades has a leading edge positioned at the forefront in the rotational direction of the blade and a blade positioned at the radially outer end of the blade. The intersection point with the end is located on the front side in the rotational direction with respect to the intersection point between the front edge and the outer side surface of the support part, and the connecting member is more than the end part located radially outward of the blade. positioned radially inwardly, the end portion of the central axial exhaust side of the connecting member, Than region closest to the central axis direction exhaust side in the section located in said connecting radially outward of the members of Kitsubasa located in said central axis direction exhaust side.
According to a second aspect of the present invention, in the impeller according to the first aspect of the present invention, the section located radially inward of the connecting member of the blade is the exhaust side of the blade in the central axial direction within the section. The end of the connecting member protrudes from the end of the connecting member on the exhaust side of the central axis in the exhaust direction of the central axis.
According to a third aspect of the present invention, in the impeller according to the first aspect of the invention, the end of the connecting member on the exhaust side in the central axial direction is the center of the portion of the blade that intersects the inner surface of the connecting member. It is located on the exhaust side of the central axial direction from the end on the exhaust side of the axial direction.
According to a fourth aspect of the present invention, in the impeller according to the first aspect of the invention, the end surface on the exhaust side of the central axis direction of the connecting member is more centrally located than the end portion on the exhaust side of the central axis direction of the blade. Located on the direction exhaust side.
According to a fifth aspect of the present invention, in the impeller according to any one of the first to fourth aspects of the present invention, the connecting member starts from the root of the blade with reference to the blade length along the radial direction of the blade. On the radially outer side, it is formed at a distance of about 70% to about 90% of the blade length.
According to a sixth aspect of the invention, in the impeller according to any one of the first to fourth aspects of the invention, in each of the plurality of blades, the trailing edge located at the rearmost in the rotation direction of the blade and the blade An intersection point with the end is located on the front side in the rotational direction with respect to the intersection point between the front edge and the outer surface of the support portion.
According to a seventh aspect of the present invention, there is provided a fan device, the impeller according to any one of the first to sixth aspects, a motor that drives the impeller, and an outer frame that surrounds the impeller. And a support body that is provided radially inward of the outer frame body and supports the motor.

  According to the first aspect of the present invention, a plurality of blades are formed by extending radially outward from the outer surface of the support portion of the impeller, and each of the plurality of blades has a rotational direction of the blade. The intersection of the leading edge positioned at the forefront and the blade tip positioned at the radially outer end of the blade is positioned forward in the rotational direction from the intersection of the leading edge and the outer surface of the support portion. For this reason, a large moment is generated at the base of the blade due to the centrifugal force generated in each part of the blade when the impeller is rotated. However, in the impeller according to the present invention, the substantially annular connecting member is formed in a circumferential direction along an arbitrary circle centered on the central axis, and connects a plurality of blades. The moment generated at the base of the blade can be suppressed, and the blade can be prevented from being deformed and the radially outer end of the blade being displaced radially outward. As a result, air can be stably blown while suppressing the influence of centrifugal force on the blades. For example, even when the impeller rotates at a high speed, the moment generated at the base of the blade due to the influence of centrifugal force is suppressed, and air can be stably blown.

  In addition, since the substantially annular connecting member is disposed radially inward from the end portion of the blade that is located radially outward, the radially inner side and the radially outer side of the connecting member The role of wings can be divided. In the region radially inward of the connecting member, the connecting member plays the role of a venturi, so the virtual venturi (inner side surface of the connecting member) and the radially inner side of the connecting member of the blade There is no gap between the two parts. Therefore, it becomes difficult for the air flow to flow backward in a region radially inward of the connecting member. For this reason, most of the airflow which flows backward passes through the area | region of the radial direction outer side of a connection member. As a result, when the impeller is operated in the surging region, the portion located on the radially outer side of the blade connecting member can function exclusively for preventing the backflow of the air flow. Thereby, the characteristic of the impeller is improved and air can be stably blown.

According to the invention of claim 5 , in order to efficiently reinforce the influence of the centrifugal force of the blade by the connecting member, the connecting member is located at any position from the substantially central portion in the radial direction of the blade to the radially outer end. It is desirable to give to. It is also necessary to consider problems such as an increase in noise due to interference between the air flow generated by the rotation of the blades and the connecting member. As a result of the tests by the inventors of the present application, the connecting member is positioned at a distance of about 70% to about 90% of the blade length from the base of the blade to the radially outward side with respect to the blade length along the radial direction of the blade. It was found that the blades can be effectively reinforced by the connecting member against the influence of centrifugal force while suppressing problems such as an increase in noise due to the application of the connecting member.

According to the sixth aspect of the present invention, the intersection of the blade tip and the trailing edge located at the radially outer end of each of the plurality of blades is more forward in the rotational direction than the intersection of the front edge and the outer surface of the support portion. Located on the side. Thus, since the impeller according to the present invention has an extremely large degree of advancement of the blade, a large moment is generated at the base of the blade due to the centrifugal force generated at each part of the blade when the impeller is rotated. To do. However, in the impeller according to the present invention, the substantially annular connecting member is formed in a circumferential direction along an arbitrary circle centered on the central axis, and connects a plurality of blades. The moment generated at the base of the blade can be suppressed, and the blade can be prevented from being deformed and the radially outer end of the blade being displaced radially outward. As a result, even if the degree of advancement of the blade is extremely large, air can be stably blown while suppressing the influence of centrifugal force on the blade.

According to the first aspect of the present invention, the end portion of the connecting member on the exhaust side in the central axial direction is more than the portion located on the exhaust side in the central axial direction in the section located radially outward from the connecting member of the blade. Is also located on the exhaust side in the central axial direction. Therefore, when a backflow of the air flow occurs in the radially outward region of the connecting member, the connecting member effectively prevents the backflowing air flow from flowing into the radially inward region of the connecting member. Can be suppressed. As a result, the characteristics of the impeller can be further improved.

According to the second aspect of the present invention, the section located radially inward from the connecting member of the blade has an end on the exhaust side in the central axis direction of the blade in the section. A portion projecting toward the exhaust side of the central axis direction from the end portion of the slab. Therefore, the blade area of the section located on the radially inner side of the connecting member that greatly contributes to the air blowing in the blades can be increased, and thereby the air blowing ability of the impeller can be further improved.

According to the third aspect of the present invention, the end portion on the exhaust side of the central axial direction of the connecting member is in the central axial direction than the end portion on the exhaust side of the central axis in the portion where the inner surface of the connecting member of the blade intersects. Located on the exhaust side. Therefore, the connecting member effectively prevents the air flow sent out to the central axial direction exhaust side by the section on the radially inner side of the connecting member in the blades from flowing back to the radially outer side of the connecting member. The impeller characteristics can be further improved.

In the invention according to claim 4 , since the blades of the impeller largely project radially outward from the support portion, the positions of the blades in the central axis direction are likely to vary slightly due to molding errors and the like. For this reason, when the impeller is supported by the blades when the impeller is placed on the temporary temporary placement portion in the fan device assembly process, the impeller is rattled, which impedes the impeller assembly process. May occur. In this regard, the impeller according to the present invention is such that the end surface on the exhaust side of the central axis direction of the connecting member is positioned closer to the exhaust side of the central axis direction than the end portion on the exhaust side of the central axis direction of the blade. When placing on the temporary placement section, the impeller can be stably supported by the end surface on the exhaust side in the central axis direction of the connecting member, and the impeller can be placed stably on the temporary placement section.

According to the seventh aspect of the present invention, even when the degree of advancement of the impeller blades is extremely large, air can be stably blown while suppressing the influence of centrifugal force on the blades.

It is the top view seen from the central-axis direction intake side of the impeller which concerns on one Embodiment of this invention. It is a side view of the impeller of FIG. It is sectional drawing of the fan apparatus with which the impeller of FIG. 1 was used. It is a graph which shows the relationship between the air volume and a noise level, and the relationship between an air volume and static pressure about the some sample of the impeller of FIG. 1 in which the connection member was formed in the position which is different regarding radial direction. It is sectional drawing which shows the partial structure of the modification of the impeller of FIG. It is explanatory drawing regarding the impeller of FIG. It is sectional drawing which shows the partial structure of the other modification of the impeller of FIG.

  1 is a plan view of an impeller 1 according to an embodiment of the present invention as viewed from the intake side in the direction of the central axis 17, FIG. 2 is a side view of the impeller 1 of FIG. 1, and FIG. It is sectional drawing of the fan apparatus 11 in which was used.

  As shown in FIG. 3, the fan device 11 using the impeller 1 according to the present embodiment includes the impeller 1, a plurality of stationary blades 12, a motor 13, an outer frame body 14, and a support body 15. ing. The stationary blade 12, the outer frame body 14, and the support body 15 constitute a housing 16 of the fan device 11. In the present embodiment, the stationary blade 12 and the support 15 are provided on the exhaust side of the impeller 1 in the direction of the central axis 17 (the lower side in FIG. 3).

  The outer frame body 14, the support body 15, and the stationary blade 12 are formed as a continuous resin member by injection molding. A mold generally used for injection molding is mainly composed of two mold members, a movable mold and a fixed mold which are separated from the housing 16 in the direction of the central axis 17. As a result, the fan device 11 can be mass-produced at low cost.

  The outer frame body 14 is provided so as to surround the impeller 1. The support 15 is provided radially inward of the outer frame 14 and supports the motor 13 and a circuit board (not shown) that drives the motor 13.

  The stationary blade 12 connects the outer frame body 14 and the support body 15, has a wind receiving surface that extends radially outward from the support body 15 and inclines with respect to the direction of the central axis 17. Yes. The role of the stationary blade 12 is to collect the air flow generated by the rotation of the impeller 1 toward the central shaft 17, and to generate the generated air flow radially inward or radially outward. Pointing in any direction. Such a stationary blade 12 is provided on the exhaust side of the impeller 1 in the direction of the central axis 17 so as to efficiently collect air or change the direction of the air generated by the impeller 1. As a modification, the stationary blade 12 may be provided on the intake side in the direction of the central axis 17 of the impeller 1.

  The motor 13 includes a rotor magnet 18 attached to an inner surface of a support portion 21 described later of the impeller 1, and an armature 19 that generates torque between the rotor magnet 18. Such a motor 13 is accommodated in the support portion 21 of the impeller 1.

  As illustrated in FIGS. 1 to 3, the impeller 1 includes a support portion 21, a plurality of moving blades 22, and a connecting member 23. The support portion 21 has a substantially cup shape formed around the central shaft 17 and accommodates the motor 13.

  The plurality of moving blades 22 are formed to extend radially outward from the outer surface 21a of the support portion 21 with a gap in the circumferential direction around the central axis 17. The plurality of moving blades 22 rotate in the rotation direction 20 around the central axis 17 together with the support portion 21, thereby generating an air flow in the direction of the central axis 17. In the present embodiment, the air flow sucked from the upper side of FIG. 2 and FIG. 3 (center axis 17 direction intake side) is discharged to the lower side of FIG. 2 and FIG. 3 (center axis 17 direction exhaust side).

  The connecting member 23 is a substantially annular member provided to reinforce the rotor blade 22 against the influence of centrifugal force. The connecting member 23 is formed in a circumferential direction along an arbitrary circle centered on the central shaft 17 and includes a plurality of moving members. The wings 22 are connected to each other. More specifically, the connecting member 23 has a substantially cylindrical shape extending along the axial direction of the central shaft 17.

  The moving blade 22 of the impeller 1 according to the present embodiment employs a forward blade, and the form of the forward blade will be described. Each rotor blade 22 has a front edge 22 a located at the forefront in the rotation direction 20 and a rear edge 22 b located at the rearmost position in the rotation direction 20. In each rotor blade 22, a straight line L1 connecting the intersection P1 between the blade tip 22c located at the radially outer end and the rear edge 22b and the central axis 17 is formed between the front edge 22a and the outer surface 21a of the support portion 21. It is located on the front side in the rotational direction 20 with respect to the intersection P2. More specifically, when viewed from the direction of the central axis 17, when the blade 22 is divided into two parts on the basis of the straight line L <b> 2 connecting the intersection P <b> 2 and the central axis 17, the rotational direction is more than the straight line L <b> 2 of each moving blade 22. The volume of the front portion 22A located on the 20 front side is larger than the volume of the rear portion 22B located on the rear side in the rotational direction 20 with respect to the straight line L2. Each rotor blade 22 is formed of the same resin and has a uniform specific gravity.

  For example, the angle (advance angle) θ1 formed by the straight line L1 and the straight line L2 is set within a range of about 10 degrees to about 25 degrees (for example, about 15 degrees). This is determined from the trade-off of noise because the noise tends to decrease as the advance angle θ1 increases while the efficiency decreases and the rotational speed of the impeller 1 needs to be increased.

  The forward movement degree of the moving blade 22 is not limited to the configuration shown in FIG. 1, and a straight line L3 connecting the intersection point P3 between the front edge 22a of the moving blade 22 and the blade tip 22c and the central axis 17 is the leading edge. Any configuration can be adopted as long as it is a forward wing located on the front side in the rotational direction 20 with respect to the intersection P2 between the outer surface 21a of the support portion 21 and 22a.

  The number of the moving blades 22 is set to 7 for example. This is because the noise tends to be smaller when the number of the moving blades 22 is smaller, but the static pressure is lowered when the number of the moving blades 22 is small. However, the number of moving blades 22 is not limited to seven.

  As described above, since the impeller 1 according to the present embodiment has an extremely large degree of advancement of the moving blade 22, the centrifugal force generated in each part of the moving blade 22 when the impeller 1 is rotated, A large moment is generated at the base of the moving blade 22. However, in the impeller 1 according to the present embodiment, the substantially cylindrical connecting member 23 is formed in the circumferential direction along an arbitrary circle centered on the central axis 17 and connects the plurality of rotor blades 22 to each other. Therefore, each rotor blade 22 is integrated and reinforced, and the moment generated at the root of the rotor blade 22 due to the influence of centrifugal force can be suppressed, and the rotor blade 22 is deformed and the blade tip 22c of the rotor blade 22 is in the radial direction. It is possible to suppress the outward displacement. As a result, even when the degree of advancement of the moving blade 22 is extremely large, air can be stably blown while suppressing the influence of centrifugal force on the moving blade 22. For example, even when the impeller 1 is rotated at a high speed, the moment generated at the root of the moving blade 22 due to the influence of centrifugal force is suppressed and air can be stably blown.

  Further, since the substantially annular connecting member 23 is disposed on the radially inner side with respect to the blade tip 22c located on the outermost radial direction of the moving blade 22, the radial inner side and the radial direction of the connecting member 23 are disposed. The role of the rotor blade 22 can be divided on the outer side. In the region radially inward of the connecting member 23, the connecting member 23 plays a role of a venturi. Therefore, the connecting member between the virtual venturi (the inner surface 23 c of the connecting member 23) and the rotor blade 22. There is no gap between the portion located on the radially inner side of 23. Therefore, it is difficult for the air flow to flow backward in a region radially inward of the connecting member 23. For this reason, most of the airflow that flows backward passes through the region on the radially outer side of the connecting member 23. As a result, when the impeller 1 is operated in the surging region, the portion located on the radially outer side of the connecting member 23 of the rotor blade 22 can function exclusively for preventing the backflow of the air flow. As a result, the characteristics of the impeller 1 can be improved and air can be blown stably.

  Further, since the connecting member 23 has a substantially cylindrical shape extending along the axial direction of the central shaft 17, each portion of the moving blade 22 in the central shaft 17 direction can be reliably reinforced against the influence of centrifugal force. .

  Next, the formation position of the connecting member 23 in the radial direction of the rotor blade 22 will be described. In order to efficiently reinforce the influence of the centrifugal force on the moving blade 22 by the connecting member 23, the connecting member 23 is provided at any position from the substantially central portion in the radial direction of the moving blade to the radially outer end. Is desirable. It is also necessary to consider problems such as an increase in noise due to interference between the air flow generated by the rotation of the rotor blade 22 and the connecting member 23. Therefore, the inventors of the present application produced a plurality of samples A to E of the impeller 1 in which the connecting member 23 was formed at different positions in the radial direction, and tested the samples A to E.

  FIG. 4 is a graph showing the relationship between the air volume and the noise level and the relationship between the air volume and the static pressure for a plurality of samples A to E of the impeller 1 in which the connecting member 23 is formed at different positions in the radial direction. . In the graph of FIG. 4, the horizontal axis is the air volume delivered per minute (unit is cubic meter), the left vertical axis is static pressure (unit is Pascal), and the right vertical axis is noise level (unit is dB). Lines G1a to G5a indicate measurement results regarding the relationship between the air volumes of the samples A to E and the noise level, and lines G1b to G5b indicate measurement results regarding the relationship between the air volumes of the samples A to E and the static pressure. In Samples A to E, the distance Lb (see FIG. 1) from the outer surface 21a of the support portion 21 along the radial direction to the connecting member 23 with reference to the blade length La (see FIG. 1) along the radial direction of the moving blade 22. Is set to 50%, 70%, 80%, 90% and 100% of the blade length La.

  When attention is paid to the relationship between the air volume and the noise level in the test results shown in FIG. 4, the samples A and E corresponding to the positions of the connecting members 23 corresponding to 50% and 100% correspond to 70%, 80%, and 90%, respectively. It can be seen that the noise is increased compared to samples B, C, and D. The reason for the increase in noise in Sample A is considered to be that the interference between the connecting member 23 and the air flow increases because the contribution of the air flow generation is large in the central portion in the radial direction of the rotor blade 22. Further, the noise increases in the sample E when the connecting member 23 is provided at the radially outer end of the rotor blade 22 in the gap between the connecting member 23 and the outer frame body 14 in the radial direction of the connecting member 23. Since the air flow in the opposite direction to the opposite side flows, it is considered that the air flow flowing in the opposite direction causes noise.

  Therefore, the connecting member 23 is separated from the root of the moving blade 22 by a distance of about 70% to about 90% of the blade length La outward in the radial direction from the blade length La along the radial direction of the moving blade 22. It has been found that if it is formed at the position, the moving blade can be effectively reinforced by the connecting member 23 against the influence of centrifugal force while suppressing problems such as an increase in noise due to the application of the connecting member 23. More preferably, the connecting member 23 is formed at a position corresponding to about 80% of the blade length La from the root of the moving blade 22. As a result, the rotor blade 22 can be reinforced by the connecting member 23 while maintaining the characteristics near the highest efficiency point where the air volume per unit power consumption is the highest.

  Moreover, in this embodiment, the support part 21, the some moving blade 22, and the connection member 23 of the impeller 1 are formed as a continuous resin member by injection molding. As the injection mold, a mold mainly composed of two mold members, that is, a movable mold and a fixed mold which are separated from the impeller 1 in the direction of the central axis 17 is used.

  As described above, since the support portion 21, the plurality of moving blades 22 and the connecting member 23 of the impeller 1 are formed of resin members, the impeller 1 can be manufactured at low cost by injection molding or the like, and the weight of the impeller 1 can be reduced. Can be planned. Moreover, since the support part 21, the several moving blades 22, and the connection member 23 of the impeller 1 are formed by the resin-made members continuous by injection molding, the impeller 1 can be mass-produced at low cost.

  Further, in the present embodiment, as shown in FIG. 3, the opening on the intake side and the exhaust side in the central axis 17 direction on the inner side surface 14 a of the outer frame body 14 has a diameter as the distance from the impeller 1 increases in the central axis 17 direction. Expanded diameter portions 14b and 14c that expand outward in the direction are provided. Further, the radially outer end of the stationary blade 12 is coupled to the enlarged diameter portion 14c on the exhaust side of the central axis 17 direction. In such a configuration, when the housing 16 is viewed from the central axis 17, a portion that becomes a blind spot of the stationary blade 12 is generated at a joint portion between the stationary blade 12 and the enlarged diameter portion 14 c. As described above, since the housing 16 is formed by injection molding using mainly two mold members that are released in the direction of the central axis 17, the molten resin is injected into the blind spots, and the resin The pedestal is formed by cooling and solidifying. Noise may be generated when the moving blade 22 of the impeller 1 rotating in the vicinity of the pedestal portion passes.

  Therefore, in the impeller 1 according to the present embodiment, as shown in FIGS. 1 and 3 and the like, the intersection point P1 between the blade tip 22c and the trailing edge 22b of the moving blade 22 and the vicinity thereof are rounded and curved. . Thereby, the noise generated when the rotor blade 22 of the rotating impeller 1 passes in the vicinity of the pedestal portion can be effectively reduced.

  In the present embodiment, as shown in FIGS. 2 and 3, the end surface 23 a on the exhaust side in the central axis 17 direction of the connecting member 23 of the impeller 1 is more than the end 22 d on the exhaust side in the central axis 17 direction of the rotor blade 22. Is also located on the exhaust side in the direction of the central axis 17.

  Since the rotor blades 22 of the impeller 1 project greatly outward in the radial direction from the support portion 21, the positions of the rotor blades 22 in the direction of the central axis 17 are likely to vary slightly due to molding errors and the like. For this reason, when the impeller 1 is supported by the rotor blades 22 when the impeller 1 is placed on the temporary temporary placement part in the assembly process of the fan device 11, the impeller 1 is rattled. There is a risk that the assembly process 1 will be hindered. In this regard, in the impeller 1 according to the present embodiment, when the impeller 1 is placed on the temporary temporary placement portion, the end surface 23a on the exhaust side in the central axis 17 direction of the connecting member 23 is brought into contact with the temporary placement portion. The impeller 1 can be stabilized and placed on the temporary placement portion. As a modification regarding this point, the end surface 23 b on the intake side in the central axis 17 direction of the connecting member 23 may be positioned closer to the intake side in the central axis 17 direction than the end portion 22 e on the intake side in the central axis 17 direction of the moving blade 22. .

  It should be noted that both the end surfaces 23a and 23b on the intake side and the exhaust side of the central shaft 17 direction of the connecting member 23 are exhausted in the direction of the central axis 17 than the end portions 22d and 22e on the exhaust side and the intake side of the moving blade 22. Or only one of the end surfaces 23a, 23b on the intake side and the exhaust side of the connecting member 23 in the direction of the central axis 17 of the connecting member 23, or the intake side or the intake side of the rotor blade 22 in the direction of the central axis 17 The end portions 22d and 22e on the side may protrude toward the exhaust side or the intake side in the direction of the central axis 17.

  Next, a modified example of the impeller 1 according to the above-described embodiment will be described with reference to FIGS. In the modification shown in FIG. 5, the end surface 23 a on the exhaust side in the direction of the central axis 17 of the connecting member 23 is positioned closest to the exhaust side of the central axis in the section 31 positioned radially outward from the connecting member 23 of the moving blade 22. It is located on the exhaust side in the direction of the central axis 17 with respect to the portion 31a. Therefore, when a backflow of the air flow is generated in the radially outer region of the connecting member 23, the backflowing air flow is, for example, as shown by an arrow 32 in FIG. The flow into the region on the side can be effectively suppressed by the portion on the exhaust side in the direction of the central axis 17 of the connecting member 23. As a result, the characteristics of the impeller 1 can be further improved.

  In the modification shown in FIG. 5, the section 33 positioned radially inward of the connecting member 23 of the moving blade 22 is the end portion 22 d on the exhaust side in the central axis 17 direction of the moving blade 22 in the section 33. The connecting member 23 has a portion 33a that protrudes toward the exhaust side in the central axis 17 direction from the end surface 23a on the exhaust side in the central axis 17 direction. In the configuration shown in FIG. 5, the end 22 d on the exhaust side in the central axis 17 direction of the portion 33 a in the section 33 of the moving blade 22 protrudes from the end surface 23 a of the connecting member 23 by the predetermined dimension D1 toward the exhaust side in the central axis 17. ing. With such a configuration, the blade area of the section 33 located on the radially inner side of the connecting member 23 that greatly contributes to the air blowing in the rotor blade 22 can be increased, and thereby the air blowing ability of the impeller 1 can be further improved. Can do.

  Further, in the modification shown in FIG. 5, the end portion on the exhaust side of the central axis 17 direction of the connecting member 23 is the end portion on the exhaust side of the central axis 17 direction of the portion where the end surface 23 a on the exhaust side in the central axis intersects the inner surface 23 c of the connecting member 23. It is located on the exhaust side in the direction of the central axis 17 from 22f. Therefore, the air flow sent to the exhaust side in the direction of the central axis 17 by the section 33 on the inner side in the radial direction of the connecting member 23 in the moving blade 22 is, for example, as shown by the arrow 34 in FIG. It is possible to effectively suppress the reverse flow around the outer side in the direction by the exhaust side portion of the connecting member 23 in the direction of the central axis 17. As a result, the characteristics of the impeller 1 can be further improved.

  Further, in the modification shown in FIG. 5, in all sections 33 positioned radially inward from the connecting member 23 of the moving blade 22, the end portion on the intake side in the central axis 17 direction of the moving blade 22 in the section 33. 22e is located on the exhaust side in the direction of the central axis 17 relative to the end surface 23b on the intake side in the direction of the central axis 17 of the connecting member 23. In the configuration shown in FIG. 5, the end surface 23 b of the connecting member 23 is predetermined on the intake side in the direction of the central axis 17 rather than the portion 22 g on the intake side in the direction of the central axis 17 at the portion where the inner surface 23 c of the connecting member 23 of the moving blade 23 intersects. Only the dimension D2 is overhanging. With such a configuration, the air flow to be drawn into the radially inner region of the connecting member 23 on the intake side in the direction of the central axis 17 of the rotor blade 22 is, for example, as shown by the arrow 35 in FIG. Escape to the radially outward side of 23 can be effectively suppressed by the portion of the connecting member 23 on the intake side in the direction of the central axis 17. As a result, the characteristics of the impeller 1 can be further improved.

  Moreover, the modification shown in FIG. 7 is proposed as a further modification of the impeller 1 shown in FIG. In the modification shown in FIG. 7, the end 22 f on the exhaust side of the central axis 17 direction of the rotor blade 22 and the end surface 23 a on the exhaust side of the central axis 17 direction of the connection member 23. Are at substantially the same position with respect to the direction of the central axis 17. Therefore, the blade area of the section 33 located on the radially inner side of the connecting member 23 that greatly contributes to the air blowing in the rotor blade 22 can be increased, and thereby the air blowing ability of the impeller 1 can be further improved.

  DESCRIPTION OF SYMBOLS 1 Impeller, 11 Fan apparatus, 12 Stator blade, 13 Motor, 14 Outer frame body, 14a Inner side surface, 14b, 14c Expanded diameter part, 15 Support body, 16 Housing, 17 Center shaft, 18 Rotor magnet, 19 Armature, 20 Rotation direction, 21 support part, 21a outer surface, 22 blade, 22A front part, 22B rear part, 22a front edge, 22a rear edge, 22b rear edge, 22c blade edge, 22d, 22e end part, 23 connecting member, 23a, 23b end surface, 23c inner surface, 23f, 23g end, 31 section, 33 section, 33a site.

Claims (7)

An impeller,
A support formed around the central axis;
A plurality of blades that are formed to extend radially outward from the outer surface of the support portion, and that generate an air flow in the central axis direction by rotating around the central axis together with the support portion;
A substantially annular connecting member formed in a circumferential direction along an arbitrary circle centered on the central axis, and connecting the plurality of blades;
With
In each of the plurality of blades, the intersection of the leading edge positioned at the forefront in the rotational direction of the blade and the blade tip positioned at the radially outer end of the blade is the leading edge and the outer surface of the support portion. Located on the front side in the rotational direction from the intersection with
The connecting member is located on the radially inner side from the end portion located on the outermost radial direction of the blade ,
The end of the connecting member on the exhaust side in the central axial direction has the exhaust in the central axial direction with respect to the portion located on the exhaust side of the central axis in the section located radially outward of the connecting member of the blade. Impeller characterized by being located on the side . The impeller according to claim 1,
The section of the blade that is located radially inward of the connecting member is such that the end of the blade in the central axial direction on the exhaust side in the section is more than the end of the connecting member on the exhaust side of the central axis. An impeller having a portion projecting toward the exhaust side in the central axial direction . The impeller according to claim 1 ,
An end of the connecting member on the exhaust side on the central axial direction is positioned closer to the exhaust side of the central axial direction than an end on the exhaust side of the central axis in a portion of the blade that intersects the inner surface of the connecting member. impeller, characterized by that. The impeller according to claim 1 ,
An impeller characterized in that an end face on the exhaust side of the central axis direction of the connecting member is located on the exhaust side of the central axis direction with respect to an end portion on the exhaust side of the central axis direction of the blade . The impeller according to any one of claims 1 to 4,
The connecting member is formed at a distance of about 70% to about 90% of the blade length radially outward from the base of the blade, with reference to the blade length along the radial direction of the blade. Impeller characterized by. The impeller according to any one of claims 1 to 4 ,
In each of the plurality of blades, the intersection of the trailing edge located at the rearmost direction of the blade and the blade tip is forward in the rotation direction than the intersection of the leading edge and the outer surface of the support portion. Impeller characterized by being located on the side . A fan device,
  The impeller according to any one of claims 1 to 6,
  A motor for driving the impeller;
  An outer frame surrounding the impeller;
  A support that is provided radially inward of the outer frame and supports the motor;
A fan device comprising:

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