JP2015108361A - Impeller and blower - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide an impeller and a blower capable of improving an air blowing amount without changing a shape of a blade body.SOLUTION: An axial flow type impeller 3 has: a plurality of blades 40; and a first auxiliary blade 50 and a second auxiliary blade 60 protruding from a blade surface of the blade and extending in a circumferential direction. The first auxiliary blade is arranged radially outside of the second auxiliary blade, and at least one part overlaps with the second auxiliary blade in a radial direction. Also, a difference between a distance from a first front end which is located at a foremost side in a rotational direction of the first auxiliary blade to a rotary shaft and a distance from a second front end which is located at a foremost side in a rotational direction of the second auxiliary blade to the rotary shaft is larger than a difference between a distance from a first rear end which is located at a rear-most side in the rotational direction of the first auxiliary blade to the rotary shaft and a distance from a second rear end which is located at a rear-most side in the rotational direction of the second auxiliary blade to the rotary shaft.

Description

  The present invention relates to an axial-flow impeller and a blower.

  Conventionally, axial fans such as fans, circulators, and diffusers that generate airflow by rotating blades are known. In addition to these air blowers for air conditioning, axial flow blowers are known that are mounted on automobiles, OA equipment, etc., and cool various devices such as engines and electrical parts. A conventional axial blower is described in, for example, Japanese Translation of PCT International Publication No. 2011-513618.

Special table 2011-513618 gazette

  In recent years, blowers for air conditioning have been required to be compact as the houses and offices become narrower. On the other hand, in a blower for cooling a device, there is a demand for improving the blown amount without increasing the size of the blower due to an increase in the amount of heat generated with the performance improvement of each device.

  A conventional blower such as a cooling fan described in JP 2011-513618A does not have a mechanism for improving the amount of air blown by blades (blades). For this reason, in the conventional blower, the air volume of the generated wind is determined only by the shape and area of the blade (blade). However, if the shape of the blade body is designed to improve the air flow without increasing the size of the blower, problems such as rigidity and resistance may occur. For this reason, there is a need for a technique for improving the air flow without greatly changing the shape of the blade body.

  An object of the present invention is to provide an impeller and a blower that can improve the amount of air flow without changing the shape of the blade body.

  An exemplary first invention of the present application is an axial-flow impeller that rotates about a rotation shaft, and projects from a blade surface of a plurality of blades arranged in the circumferential direction and the blade in the circumferential direction. A first auxiliary wing and a second auxiliary wing extending, wherein the first auxiliary wing and the second auxiliary wing are disposed on at least one of a pressure surface side and a suction surface side of the blade, and The auxiliary wing is arranged on the radially outer side of the second auxiliary wing, and at least a part of the auxiliary wing overlaps with the second auxiliary wing in the radial direction, and is located at the foremost rotation direction of the first auxiliary wing. The difference between the distance from the rotation axis to the rotation axis and the distance from the second front end located in the foremost rotation direction of the second auxiliary wing to the rotation axis is located in the foremost rotation direction of the first auxiliary wing. The distance from the first rear end to the rotating shaft and the most rotational direction of the second auxiliary wing Than the difference between the distance from the second rear end to said rotary shaft located towards large, an impeller.

  According to the exemplary first invention of the present application, the distance between the two auxiliary blades becomes narrower from the front to the rear in the rotational direction. Thus, by concentrating the axial airflow generated by the blades between the two auxiliary blades, a portion having a high wind speed is generated in the airflow. The part with a high wind speed draws in the surrounding gas due to the Coanda effect, so that the air volume of the airflow toward the front side in the axial direction can be increased.

FIG. 1 is a side view of the electric fan according to the first embodiment. FIG. 2 is a perspective view of the impeller according to the first embodiment. FIG. 3 is a front view of the impeller according to the first embodiment. FIG. 4 is a rear view of the impeller according to the first embodiment. FIG. 5 is a partial side view of the impeller according to the first embodiment. FIG. 6 is a front view of an impeller according to a modification. FIG. 7 is a rear view of an impeller according to a modification. FIG. 8 is a partial side view of an impeller according to a modification. FIG. 9 is a rear view of an impeller according to a modified example. FIG. 10 is a rear view of an impeller according to a modification. FIG. 11 is a rear view of an impeller according to a modification. FIG. 12 is a rear view of an impeller according to a modification. FIG. 13 is a rear view of an impeller according to a modification. FIG. 14 is a rear view of an impeller according to a modified example.

  Hereinafter, exemplary embodiments of the present invention will be described with reference to the drawings. In the present application, a direction parallel to the rotation axis is referred to as an “axial direction”, a direction orthogonal to the rotation axis is referred to as a “radial direction”, and a direction along an arc centered on the rotation axis is referred to as a “circumferential direction”. Further, in the present application, the shape and positional relationship of each part will be described with the pressure surface side of the impeller that is one side in the axial direction as the front side and the negative pressure surface side of the impeller that is the other side in the axial direction as the back side. However, the definition of the front side and the back side is not intended to limit the orientation when using the impeller and the blower according to the present invention.

<1. First Embodiment>
<1-1. Overall structure of electric fan>
FIG. 1 is a side view of a fan 1 according to the first embodiment of the blower of the present invention. FIG. 2 is a perspective view of the impeller 3 of the electric fan 1. FIG. 3 is a front view of the impeller 3. FIG. 4 is a rear view of the impeller 3. 1 to 4, the rotation direction is indicated by a solid arrow.

  The electric fan 1 is a device that rotates the impeller 3 with the power of the motor 2 and sends wind to the front side of the impeller 3. The electric fan 1 is used, for example, for directing the user directly to cool the user. Moreover, the electric fan 1 may be used as a circulator used with an air conditioner etc. As shown in FIG. 1, the electric fan 1 of the present embodiment includes a motor 2 and an axial flow type impeller 3.

  The motor 2 is a mechanism that supplies power for rotation to the impeller 3. In the present embodiment, a brushless DC motor is used for the motor 2. A brushless DC motor has a longer life than a motor with a brush because there is no performance deterioration due to wear of the brush. Further, the brushless DC motor is easier to shift than the AC motor, and it is easy to reduce power consumption.

  The motor 2 includes a stationary part 21 and a rotating part 22 that rotates about the rotating shaft 9. The stationary part 21 has a motor casing 211 that houses an armature of the motor and a part of the rotating part 22 such as a rotor.

  The rotating unit 22 includes a rotor that generates torque with the armature, and a shaft 221 that extends along the rotating shaft 9. The shaft 221 is fixed to the rotor inside the motor casing 211. An end portion on the front side of the shaft 221 protrudes from the motor casing 211 to the front side, and is fixed to a center portion 30 described later of the impeller 3. For this reason, when the motor 2 is driven, the impeller 3 rotates around the rotating shaft 9 together with the rotating portion 22 of the motor 2. In the present embodiment, the front end of the shaft 221 is fixed to the impeller 3, but a portion other than the front end of the shaft 221 may be fixed to the impeller 3. That is, it is only necessary that a part of the shaft 221 and the impeller 3 are fixed.

  The impeller 3 is supported so as to be rotatable with respect to the stationary portion 21 of the motor 2. The impeller 3 generates an air flow from the back side to the front side by rotating in the rotation direction indicated by the solid line arrow in FIGS. As shown in FIGS. 1 to 4, the impeller 3 includes a central portion 30, a plurality of blades 40, a first auxiliary wing 50, and a second auxiliary wing 60.

  The impeller 3 of the present embodiment is made of resin and is molded by injection molding. For this reason, the center part 30, the some blade | wing 40, the 1st auxiliary blade 50, and the 2nd auxiliary blade 60 are formed as a single member. The impeller 3 may be formed of other materials such as metal. The impeller 3 may be formed by combining a plurality of components.

  As shown in FIGS. 2 and 4, the central portion 30 includes a disc-shaped disc portion 301 centering on the rotation shaft 9, and a wall portion 302 extending from the edge of the disc portion 301 to the axially rear side. Have That is, the center part 30 of this embodiment is a covered cylindrical shape. As shown in FIG. 4, the central portion 30 further includes a cylindrical portion 303 and a rib 304. The cylindrical portion 303 protrudes in a substantially cylindrical shape from the disc portion 301 toward the back side. Due to the shape, the central portion 30 has a shaft hole 31 that is an internal space of the tubular portion 303 at a substantially central portion on the back side. The shaft 221 of the motor 2 is inserted into the shaft hole 31 and fixed. For this reason, when the motor 2 is driven, the impeller 3 rotates around the rotation shaft 9 together with the shaft 221. The wall portion 302 and the tubular portion 303 are connected by a plurality of radially extending ribs 304. Thereby, it is suppressed that the cylindrical part 303 is distorted with respect to the rotating shaft 9. That is, the impeller 3 is suppressed from being distorted with respect to the shaft 221.

  In addition, in this embodiment, although the center part 30 was substantially circular seeing from the front side, this invention is not limited to this. The central portion 30 may be a polygon such as a pentagon or a hexagon as viewed from the front side. Moreover, in this embodiment, although the edge part of the front side of the shaft 221 is arrange | positioned inside the center part 30, if the shaft 221 and the center part 30 are being fixed, the edge part of the front side of the shaft 221 will be You may protrude from the center part 30 to the front side.

  As shown in FIGS. 3 and 4, each of the plurality of blades 40 extends radially outward from the side surface of the central portion 30. The plurality of blades 40 are arranged at substantially equal intervals in the circumferential direction. However, the intervals in the circumferential direction of the plurality of blades 40 are not necessarily constant. As shown in FIGS. 2 and 4, a first auxiliary blade 50 and a second auxiliary blade 60, which are a pair of auxiliary blades, are disposed on the suction surface 42 side of each blade 40. Detailed configurations and operations of the first auxiliary blade 50 and the second auxiliary blade 60 will be described later.

  As shown in FIGS. 1 and 2, each blade 40 is inclined from the back side to the front side as it goes from the front edge 401 to the rear edge 402. Here, the front edge 401 is an end edge portion on the front side in the rotation direction of the blade 40, and the rear edge 402 is an end edge portion on the rear side in the rotation direction of the blade 40. With this shape, when the impeller 3 rotates, the pressure near the pressure surface 41 that is the blade surface on the front side of the blade 40 increases, and the pressure near the suction surface 42 that is the blade surface on the back side of the blade 40 decreases. Become. Thereby, in the circumference | surroundings of the blade | wing 40, the airflow which goes to an axial direction generate | occur | produces from the back side to the front side.

<1-2. Auxiliary wing>
Next, detailed configurations and operations of the first auxiliary blade 50 and the second auxiliary blade 60 will be described. FIG. 5 is a partial side view of the impeller 3. In FIG. 5, the tangent line is shown.

  As shown in FIG. 2, the first auxiliary blade 50 and the second auxiliary blade 60 protrude from the negative pressure surface 42 of the blade 40 toward the back side. The first auxiliary wing 50 and the second auxiliary wing 60 extend in the circumferential direction. The first auxiliary wing 50 is disposed on the radially outer side of the second auxiliary wing 60. Further, a part of the first auxiliary wing 50 and a part of the second auxiliary wing 60 overlap in the radial direction.

  As shown in FIG. 4, in a plan view from the axial direction, the portion of the first auxiliary wing 50 that is positioned most forward in the rotational direction is the first front end 51, and the portion of the first auxiliary wing 50 that is positioned most rearward in the rotational direction is. A portion of the first rear end 52 and the second auxiliary wing 60 that is positioned forward in the rotational direction is referred to as a second front end 61, and a portion of the second auxiliary wing 60 that is positioned rearward in the rotational direction is referred to as a second rear end 62.

  The difference between the radial distance D1 from the first front end 51 to the rotary shaft 9 and the radial distance D2 from the second front end 61 to the rotary shaft 9 is the radial distance from the first rear end 52 to the rotary shaft. It is larger than the difference between D3 and the radial distance D4 from the second rear end 62 to the rotary shaft 9. That is, the radial distance between the first auxiliary blade 50 and the second auxiliary blade 60 decreases from the front to the rear in the rotational direction. Thereby, the axial airflow generated by the blades 40 is concentrated between the first auxiliary blade 50 and the second auxiliary blade 60.

  Therefore, as indicated by the white arrow in FIG. 1, in the vicinity of the radial position where the first auxiliary blade 50 and the second auxiliary blade 60 are disposed, the radial position where the other portion of the blade 40 is disposed. As compared with the above, the wind speed of the axial air flow generated by the blades 40 is increased. As a result, as indicated by a dashed white arrow in FIG. 1, the air flow having a high wind speed draws in the surrounding gas due to the Coanda effect. Therefore, the air volume of the airflow which goes to the front side in the axial direction increases.

  That is, in this electric fan 1, by providing the 1st auxiliary | assistant wing | blade 50 and the 2nd auxiliary | assistant wing | blade 60, without changing the main body shape of the blade | wing 40, and without increasing the rotation speed of the motor 2, the ventilation volume Can be increased.

  In the first auxiliary blade 50 of the present embodiment, the distance D1 is greater than the distance D3. Thus, the first auxiliary blade 50 has a function of guiding the axial airflow generated by the blades 40 radially inward of the first auxiliary blade 50 inward in the radial direction. In the second auxiliary blade 60 of the present embodiment, the distance D2 is smaller than the distance D4. Accordingly, the second auxiliary blade 60 has a function of guiding the axial airflow generated by the blades 40 on the radially outer side than the second auxiliary blade 60 to the radially outer side. By such a guide function of the first auxiliary blade 50 and the second auxiliary blade 60, the axial airflow generated by the blades 40 is efficiently concentrated. Therefore, in the vicinity of the radial position surrounded by the first auxiliary blade 50 and the second auxiliary blade 60, the velocity of the airflow in the axial direction can be increased efficiently.

  Further, the first auxiliary blade 50 of the present embodiment is disposed along the blade outer edge portion 403 on the radially outer side of the blade 40. That is, the first outer edge portion 501 on the radially outer side of the first auxiliary blade 50 overlaps the blade outer edge portion 403 in the axial direction. As described above, the first auxiliary blade 50 is arranged in the vicinity of the radially outer side of the blade 40, so that the wind speed of the outermost portion of the airflow sent by the blade 40 toward the front side in the axial direction is increased. Therefore, air on the outer side in the radial direction than the blades 40 is more likely to be drawn in by the air flow having a high wind speed. That is, the amount of airflow toward the front side in the axial direction is further increased.

  In the present embodiment, almost the entire first outer edge portion 501 overlaps the blade outer edge portion 403 in the axial direction, but a very small portion of the first outer edge portion 501 overlaps the blade outer edge portion 403 in the axial direction. May be.

  As shown in FIG. 4, the first front end 51 of the first auxiliary blade 50 and the second front end 61 of the second auxiliary blade 60 are located behind the front edge 401 of the blade 40 in the rotational direction. That is, the front edge 401 of the blade 40 does not overlap the first front end 51 and the second front end 61 in the axial direction. Therefore, the same relative airflow generated in the direction opposite to the rotation direction due to the rotation of the blade 40 does not strike the front edge 401, the first front end 51, and the second front end 61 at the same time. Thereby, compared with the case where the front edge 401, the 1st front end 51, and the 2nd front end 61 overlap in an axial direction, the blade 40, the 1st auxiliary wing 50, and the 2nd auxiliary wing 60 are when the wind is torn. Interference sound is reduced.

  Further, a part including the first front end 51 of the first auxiliary blade 50 has a curved surface without corners. Since the vicinity of the first front end 51 of the first auxiliary blade 50 is rounded, the interference sound that cuts off the wind is suppressed in the vicinity of the first front end 51. In addition, the strength of the first auxiliary blade 50 is higher than that in the case where the vicinity of the first front end 51 has a sharp shape. Similarly for the second auxiliary wing 60, a part including the second front end 61 of the second auxiliary wing 60 has a curved surface with no corners. For this reason, the interference sound resulting from the 2nd auxiliary blade 60 is also suppressed. In addition, the strength of the second auxiliary blade 60 is improved as compared with the case where the vicinity of the second front end 61 has a sharp shape.

  Further, as shown in FIG. 5, the first auxiliary blade 50 and the second auxiliary blade 60 gradually decrease as they move away from the suction surface 42 of the blade 40 toward the back surface side. That is, the first auxiliary wing 50 and the second auxiliary wing 60 gradually decrease with distance from the blade surface of the blade 40 in the axial direction. Thereby, generation | occurrence | production of the turbulent flow in the 1st auxiliary blade 50 and the 2nd auxiliary blade 60 vicinity can be suppressed. Further, when the impeller 3 is molded by injection molding, the mold can be pulled out on the back side in the axial direction around the first auxiliary blade 50 and the second auxiliary blade 60. As a result, injection molding becomes easy, and an increase in the parting line due to the use of a complicated mold can be suppressed.

<2. Modification>
As mentioned above, although exemplary embodiment of this invention was described, this invention is not limited to said embodiment.

  FIG. 6 is a front view of an impeller 3A according to a modification. In the example of FIG. 6, the first auxiliary blade 50A and the second auxiliary blade 60A protrude from the pressure surface 41A of the blade 40A toward the front side. Thus, the first auxiliary wing and the second auxiliary wing may be arranged on the pressure surface side.

  In the example of FIG. 6 as well, the difference between the radial distance from the first front end 51A to the rotary shaft 9A and the radial distance from the second front end 61A to the rotary shaft 9A is from the first rear end 52A to the rotary shaft 9A. Is greater than the difference between the distance in the radial direction and the distance in the radial direction from the second rear end 62A to the rotating shaft 9A.

  Thereby, in the vicinity of the radial position where the first auxiliary blade 50A and the second auxiliary blade 60A are arranged, the axial direction generated by the blade 40A is larger than the radial position where other parts of the blade 40A are arranged. The wind speed of the air current increases. As a result, the airflow with the high wind speed draws in the surrounding gas due to the Coanda effect. Therefore, the air volume of the airflow toward the front side in the axial direction increases.

  FIG. 7 is a rear view of an impeller 3B according to another modification. FIG. 8 is a partial side view of the impeller 3B in the example of FIG. In the example of FIG. 7, the first front end 51B of the first auxiliary wing 50B and the second front end 61B of the second auxiliary wing 60B are located behind the front edge 401B of the blade 40B in the rotational direction. Further, the first rear end 52B of the first auxiliary wing 50B and the second rear end 62B of the second auxiliary wing 60B are located in front of the rear edge 402B of the blade 40B in the rotational direction. That is, the first front end 51B, the first rear end 52B, the second front end 61B, and the second rear end 62B are all disposed inside the blade 40B when viewed from the axial direction.

  For this reason, when the impeller 3B is molded by injection molding, no parting line is generated in the first auxiliary blade 50B and the second auxiliary blade 60B. Therefore, the parting line of the impeller 3B as a whole does not increase compared to the case where the blade 40B does not have the first auxiliary blade 50B and the second auxiliary blade 60B.

  Further, as shown in FIG. 8, the axially front end 54B of the first auxiliary wing 50B and the axially front end 64B of the second auxiliary wing 60B are respectively axially front of the blade 40B. It is located on the rear side in the axial direction from the end 43B on the side. Further, the axially back end 55B of the first auxiliary wing 50B and the axially back end 65B of the second auxiliary wing 60B are more than the axially back end 44B of the blade 40B, respectively. Located on the front side in the axial direction. That is, the axial existence region 56B of the first auxiliary blade 50B and the axial existence region 66B of the second auxiliary blade 60B are located within the range of the axial existence region 45B of the blade 40.

  Thereby, compared with the case where the impeller 3B does not have the 1st auxiliary blade 50B and the 2nd auxiliary blade 60B, the distance of the impeller 3B and the stationary member arrange | positioned around the impeller 3B is not shortened. Therefore, an increase in noise due to interference with the stationary member is suppressed. Further, the space for disposing the stationary member is not limited by the first auxiliary blade 50B and the second auxiliary blade 60B. In addition, as a stationary member arrange | positioned around the impeller 3B, the motor, the housing which accommodates the impeller 3B, etc. are assumed, for example.

  FIG. 9 is a rear view of an impeller 3C according to another modification. In the example of FIG. 9, the first rear end 52C of the first auxiliary blade 50C and the second rear end 62C of the second auxiliary blade 60C are located behind the rear edge 402C of the blade 40C in the rotational direction. In the example of FIG. 9, the axial airflow generated by the blade 40C is guided by the first auxiliary blade 50C and the second auxiliary blade 60C even after leaving the rear edge 402C of the blade 40C rearward in the rotational direction. . Therefore, the function of concentrating the airflow generated by the blade 40C can be enhanced.

  In addition, the first rear end 52C and the second rear end 62C are disposed outside the blade 40C when viewed from the axial direction, so that the circumferential lengths of the first auxiliary blade 50C and the second auxiliary blade 60C are increased. Take long. Thereby, the guide function of the airflow by the first auxiliary blade 50C and the second auxiliary blade 60C can be further enhanced.

  FIG. 10 is a rear view of an impeller 3D according to another modification. In the example of FIG. 10, the first auxiliary blade 50D does not overlap with the blade outer edge portion 403D on the radially outer side of the blade 40D. In other words, the first auxiliary blade 50D is not located near the outermost radial direction of the blade 40D. As described above, the first auxiliary blade 50D may be located on the radially inner side of the blade outer edge portion 403D of the blade 40D.

  FIG. 11 is a rear view of an impeller 3E according to another modification. In the example of FIG. 11, the radial position of the second auxiliary blade 60 </ b> E is radially outside of half of the blade 40 </ b> E. Specifically, the following dimensional relationship is satisfied.

  In a plan view from the axial direction, the outermost end portion 404E of the blade 40E is the outermost end portion of the blade 40E, and the innermost portion of the blade 40E is the innermost portion of the blade 40E. A portion located at the innermost radial direction of 405E and the second auxiliary blade 60E is defined as a second inner end portion 63E.

  In the example of FIG. 11, the difference between the radial distance D5 between the second inner end portion 63E and the rotary shaft 9E and the radial distance D6 between the blade outer end portion 404E and the rotary shaft 9E is as follows: It is smaller than half of the difference between the distance D7 between the radial direction 405E and the rotating shaft 9E and the distance D6. That is, assuming that the position at which the distance from the rotation shaft 9E is exactly halfway between the distance D6 and the distance D7 is the position D0, the second inner end 63E of the second auxiliary blade 60E is radially outward from the position D0. To position.

  Thereby, in the airflow sent out by the blade 40E toward the front side in the axial direction, the portion where the wind speed is increased by the first auxiliary blade 50E and the second auxiliary blade 60E becomes more radially outward. Therefore, air on the outer side in the radial direction is more likely to be drawn in than the blades 40E due to the high air velocity. That is, the amount of airflow toward the front side in the axial direction is further increased.

  FIG. 12 is a rear view of an impeller 3F according to another modification. In the example of FIG. 12, the first auxiliary blade 50F has a flat plate shape with a constant blade thickness except for the vicinity of the first front end 51F and the vicinity of the first rear end 52F. Similarly, the second auxiliary blade 60F has a flat blade shape with a constant blade thickness except for the vicinity of the second front end 61F and the vicinity of the second rear end 62F. Thus, the blade thickness of the first auxiliary blade 50F and the second auxiliary blade 60F may be substantially constant.

  Also in the example of FIG. 12, the difference between the radial distance from the first front end 51F to the rotary shaft 9F and the radial distance from the second front end 61F to the rotary shaft 9F is the difference from the first rear end 52F to the rotary shaft 9F. Is greater than the difference between the distance in the radial direction and the distance in the radial direction from the second rear end 62F to the rotating shaft 9F.

  Thereby, in the vicinity of the radial position where the first auxiliary blade 50F and the second auxiliary blade 60F are arranged, the axial direction generated by the blade 40F is larger than the radial position where the other part of the blade 40F is arranged. The wind speed is high. As a result, the airflow with the high wind speed draws in the surrounding gas due to the Coanda effect. Therefore, the air volume of the airflow toward the front side in the axial direction increases.

  FIG. 13 is a rear view of an impeller 3G according to another modification. In the example of FIG. 13, the blade 40G, the first auxiliary blade 50G, and the second auxiliary blade 60G are separate members. The arrangement position of the first auxiliary blade 50G can be switched between a first orientation P1 indicated by a solid line and a second orientation P2 indicated by a broken line. Further, the arrangement position of the second auxiliary blade 60G can be switched between a third direction P3 indicated by a solid line and a fourth direction P4 indicated by a broken line.

  Here, the radial distance between the first front end 51G and the rotation shaft 9G in the first orientation P1 is D11, the radial distance between the first front end 51G and the rotation shaft 9G in the second orientation P2 is D12, and the first orientation A radial distance between the first rear end 52G and the rotating shaft 9G in P1 is D31, and a radial distance between the first rear end 52G and the rotating shaft 9G in the second orientation P2 is D32.

  In addition, the radial distance between the second front end 61G and the rotation shaft 9G in the third orientation P3 is D21, the radial distance between the second front end 61G and the rotation shaft 9G in the fourth orientation P4 is D22, and the third orientation P3. The radial distance between the second rear end 62G and the rotary shaft 9G in D4 is D41, and the radial distance between the second rear end 62G and the rotary shaft 9G in the fourth orientation P4 is D42.

  The distance D11 is substantially the same as the distance D31 or larger than the distance D31. Thereby, in the first direction P1, the first auxiliary blade 50G improves the straightness of the axial airflow generated by the blade 40G or guides the airflow radially inward. On the other hand, the distance D12 is larger than the distance D32. That is, in the second orientation P2, the first auxiliary blade 50G guides the axial airflow generated by the blade 40G inward in the radial direction. Further, the difference between the distance D12 and the distance D32 is larger than the difference between the distance D11 and the distance D31. Thereby, in the 2nd azimuth | direction P2, the guide function of the airflow of the axial direction by the 1st auxiliary blade 50G is high compared with the 1st azimuth | direction P1.

  The distance D21 is smaller than the distance D41. Further, the distance D22 is smaller than the distance D42. Thus, in the third orientation P3 and the fourth orientation P4, the second auxiliary blade 60G guides the axial airflow generated by the blade 40G outward in the radial direction. Further, the difference between the distance D22 and the distance D42 is larger than the difference between the distance D21 and the distance D41. Thereby, in the 4th azimuth | direction P4, compared with the 3rd azimuth | direction P3, the guide function of the airflow of an axial direction is high by the 2nd auxiliary blade 60G.

  Thus, in the example of FIG. 13, the first auxiliary blade 50G can be switched between the first orientation P1 and the second orientation P2, and the second auxiliary blade 60G is switched between the third orientation P3 and the fourth orientation P4. Is possible. Thereby, the radial position where the airflow generated by the blade 40G is concentrated and the speed of the airflow can be selectively switched according to the application.

  FIG. 14 is a rear view of an impeller 3H according to another modification. In the example of FIG. 14, the impeller 3H includes a third auxiliary blade 70H in addition to the first auxiliary blade 50H and the second auxiliary blade 60H in each blade 40H.

  In the example of FIG. 14, the radial distance between the first auxiliary wing 50H and the second auxiliary wing 60H decreases from the front to the rear in the rotational direction. Further, the radial distance between the second auxiliary blade 60H and the third auxiliary blade 70H becomes narrower from the front in the rotational direction toward the rear in the rotational direction. Thereby, the axial airflow generated by the blades 40 is concentrated between the first auxiliary blade 50H and the second auxiliary blade 60H and between the second auxiliary blade 60H and the third auxiliary blade 70H. Thus, three or more auxiliary wings may be arranged on each blade.

  In the electric fan of the above-described embodiment, a DC motor is used as power for rotating the impeller. However, the blower of the present invention may use an AC motor instead of the DC motor. The blower of the present invention may rotate the impeller by connecting another drive source such as an engine to the impeller instead of the motor.

  Moreover, the air blower of this invention does not necessarily need to be the fan aiming at taking coolness. For example, the blower used for other uses, such as a ceiling fan, a circulator, and a cooling fan for automobiles, may be used.

  Moreover, the shape of the detail of each member which comprises an air blower may differ from the shape shown by each figure of this application. For example, although the impeller of the above embodiment has five blades, the impeller may have other blades such as three, four, and seven blades.

  Moreover, you may combine suitably each element which appeared in said embodiment and modification in the range which does not produce inconsistency.

  The present invention can be used for an impeller and a blower.

DESCRIPTION OF SYMBOLS 1 Fan 2 Motor 3, 3A, 3B, 3C, 3D, 3E, 3F, 3G, 3H Impeller 9, 9A, 9E, 9F, 9G Rotating shaft 21 Static part 22 Rotating part 30 Central part 40, 40A, 40B, 40C, 40D, 40E, 40F, 40G, 40H Blade 41, 41A Pressure surface 42 Negative pressure surface 50, 50A, 50B, 50C, 50D, 50E, 50F, 50G, 50H First auxiliary blades 51, 51A, 51B, 51F, 51G First Front end 52, 52A, 52B, 52C, 52F, 52G First rear end 60, 60A, 60B, 60C, 60E, 60F, 60G, 60H Second auxiliary blade 61, 61A, 61B, 61F, 61G Second front end 62, 62A , 62B, 62C, 62F, 62G Second rear end 70H Third auxiliary wing 401, 401B Front edge 402, 402B, 402C Rear edge 403, 403D Blade outer edge 404E Blade outer end 405E Blade inner end 501 First outer edge

Claims (15)

An axial flow type impeller that rotates about a rotation axis,
A plurality of blades arranged in a circumferential direction;
A first auxiliary wing and a second auxiliary wing protruding from the blade surface of the blade and extending in the circumferential direction;
Have
The first auxiliary wing and the second auxiliary wing are disposed on at least one of the pressure surface side and the suction surface side of the blade,
The first auxiliary wing is disposed radially outside the second auxiliary wing, and at least a part of the second auxiliary wing overlaps in the radial direction,
A distance from the first front end positioned forward in the rotational direction of the first auxiliary wing to the rotational shaft, and a distance from the second front end positioned forward in the rotational direction of the second auxiliary wing to the rotational shaft. The difference is that the distance from the first rear end located at the rearmost in the rotational direction of the first auxiliary wing to the rotational axis and the second rear end located at the rearmost in the rotational direction of the second auxiliary wing from the rotational axis. The impeller is larger than the difference from the distance to. The impeller according to claim 1,
The impeller has a distance from the first front end to the rotating shaft that is the same as a distance from the first rear end to the rotating shaft or greater than a distance from the first rear end to the rotating shaft. The impeller according to claim 1 or 2, wherein
The impeller, wherein a distance from the second front end to the rotation shaft is the same as a distance from the second rear end to the rotation shaft or smaller than a distance from the second rear end to the rotation shaft. The impeller according to any one of claims 1 to 3,
An impeller in which at least a part of the first outer edge portion on the radially outer side of the first auxiliary wing overlaps with the blade outer edge portion on the radially outer side of the blade in the axial direction. The impeller according to any one of claims 1 to 4,
The difference between the distance from the innermost second inner end portion of the second auxiliary wing to the rotating shaft and the distance from the outermost outer blade portion of the blades to the rotating shaft is An impeller that is smaller than a half of a difference between a distance from the innermost blade inner end portion of the blade to the rotary shaft and a distance from the outer blade end to the rotary shaft. An impeller according to any one of claims 1 to 5,
The impeller, wherein the first auxiliary wing and the second auxiliary wing gradually decrease as they move away from the blade surface of the blade in the axial direction. The impeller according to any one of claims 1 to 6,
The impeller, wherein the first front end of the first auxiliary wing and the second front end of the second auxiliary wing are located behind the front edge of the blade in the rotation direction. The impeller according to any one of claims 1 to 6,
The impeller, wherein the first rear end of the first auxiliary wing and the second rear end of the second auxiliary wing are positioned forward in the rotational direction with respect to the rear edge of the blade. The impeller according to any one of claims 1 to 6,
The impeller, wherein the first rear end of the first auxiliary wing and the second rear end of the second auxiliary wing are located behind the rear edge of the blade in the rotation direction. An impeller according to any one of claims 1 to 9,
The end portion on the one axial side of the first auxiliary wing is located on the other axial side than the end portion on the one axial side of the blade,
The end portion on the other side in the axial direction of the first auxiliary wing is located on one side in the axial direction than the end portion on the other side in the axial direction of the blade,
An end portion on one side in the axial direction of the second auxiliary wing is located on the other side in the axial direction with respect to an end portion on one side in the axial direction of the blade,
An impeller, wherein an end portion on the other axial side of the second auxiliary wing is positioned on one axial side than an end portion on the other axial side of the blade. The impeller according to any one of claims 1 to 10,
The part including the first front end of the first auxiliary wing and the part including the second front end of the second auxiliary wing have a curved surface having no corners. The impeller according to any one of claims 1 to 11,
The impeller can switch the arrangement position of the first auxiliary wing between a first azimuth and a second azimuth,
The difference in the first orientation between the distance between the first front end and the rotation axis and the distance between the first rear end and the rotation axis is the distance between the first front end and the rotation axis, and the first An impeller different from the difference in the second orientation between the distance between the rear end and the rotation axis. An impeller according to any one of claims 1 to 12,
The impeller can switch the arrangement position of the second auxiliary wing between a third direction and a fourth direction,
The difference in the third direction between the distance between the second front end and the rotation axis and the distance between the second rear end and the rotation axis is the distance between the second front end and the rotation axis, and the second An impeller different from the difference in the fourth direction between the distance between the rear end and the rotation axis. An impeller according to any one of claims 1 to 13,
The impeller is made of resin and is formed by injection molding. A motor having a stationary part and a rotating part that rotates about the rotation axis;
The impeller according to any one of claims 1 to 14, wherein the impeller rotates together with the rotating part.
With blower.

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