JP5260579B2 - Electric blower and vacuum cleaner equipped with it - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide an electric blower and a vacuum cleaner mounted with the same, for improving assembling performance without collapsing manufacture of caulking by a sheet metal, by achieving high efficiency by matching between leakage of an inlet and the angle distribution of a blade, in the electric blower. <P>SOLUTION: The blade 400 has a substantially two-dimensional shape in the inlet vicinity 403 and the outlet vicinity 404, and falls down in the rotational direction 405 between the inlet vicinity 403 and the outlet vicinity 404, and the blade 400 has a crescent shape when viewed from the axial direction. <P>COPYRIGHT: (C)2011,JPO&amp;INPIT

Description

  The present invention relates to an electric blower, a vacuum cleaner on which the electric blower is mounted, and a method for manufacturing the same.

  A conventional electric blower is also shown in, for example, Patent Document 1 below, and generally includes a shroud, a main plate disposed at an opposing position thereof, and a plurality of blades disposed therebetween. The blade has a shroud side inclined more than the hub side and rotated at a high speed to obtain an air volume and a vacuum pressure.

  In particular, in Patent Document 1, the fan blade is sandwiched between the front shroud and the rear shroud and fixed by caulking, and the curvature radius of the fan blade near the suction port is larger on the front shroud side than on the rear shroud side. The front shroud side is inclined in the rotational direction on the inner peripheral side, and the rotating fan of the electric blower substantially perpendicular to the rear shroud is described on the outer peripheral side.

Japanese Patent No. 2757501 (Japanese Patent Laid-Open No. 3-151598)

  In the conventional electric blower, since detailed blade angle distribution is not adjusted with respect to the air flow at the inlet, separation and backflow phenomenon easily occur in the flow inside the fan, causing energy loss (decrease in efficiency). In particular, at the suction port of the electric blower, the leakage flow generated by the pressure difference between the blade suction port and the impeller outlet is suppressed by a rotating blower and a mouth ring for guiding the suction flow. For this reason, there is a step at the connection between the rotating body and the stationary body at the suction port. In consideration of this step flow and leakage flow, in order to adjust the matching with the blade inlet angle and the load distribution between the blades, It was necessary to understand the phenomenon and optimize the whole. That is, by adjusting the blade angle distribution by matching with the leakage in the presence of inlet leakage, it is necessary to optimize the load distribution between the blades, suppress the separation phenomenon and the backflow phenomenon, and achieve high efficiency. In addition, since the detailed fan blade angle distribution is not adjusted for the air flow at the inlet, the inclination of the fan blade does not coincide with the air inflow direction near the suction port, and the air hits the side surface of the fan blade, There is also a risk of increased collision loss.

  Further, in the electric blower, since the blade has a large inclination with respect to the main plate when viewed from the axial direction, there is an assembly problem that the blade and the caulking are easily crushed due to buckling or the like in the process of assembling with the sheet metal. It was.

  Further, in the conventional electric blower, the outer peripheral side (outflow side) is substantially perpendicular to the rear shroud even though the front shroud side is inclined in the rotational direction on the inner peripheral side (inflow side). On the side (outflow side), the air flow becomes uneven from the front shroud to the rear shroud, that is, the pressure distribution becomes non-uniform from the front shroud to the rear shroud, and the energy loss may increase.

  Accordingly, an object of the present invention is to provide an electric blower that can obtain high efficiency even when there is an inlet leak and a vacuum cleaner equipped with the electric blower.

  Another object of the present invention is to provide a method for manufacturing an electric blower with improved assembly accuracy.

  Further, the present invention provides a highly efficient electric blower with less collision loss and a vacuum cleaner equipped with the electric blower by optimizing the inclination of the inner edge of each blade with respect to the hub in the rotational direction of the formation direction. It is aimed.

  Another object of the present invention is to provide a highly efficient electric blower that suppresses the non-uniform flow of air from the shroud to the hub and reduces energy loss, and a vacuum cleaner equipped with the electric blower.

  In order to achieve the above object, the present invention is characterized by the following configurations.

That is, in the case where each blade is formed of a flat plate, the formation direction of each blade with respect to the hub is inclined in the rotation direction at the intermediate portion compared to the inner edge and the outer edge of the blade, and the formation direction at the outer edge of each blade with respect to the hub is The inclination of the blades in the direction of rotation with respect to the hub in the rotation direction is gradually increased from the inner edge toward the intermediate portion and gradually decreased from the intermediate portion toward the outer edge .

  Alternatively, the outer diameter of the impeller is in the range of φ60 mm to φ120 mm, the height with respect to the hub at the outer edge of the vane is in the range of 6 to 12 mm, and the thickness of the vane is in the range of 0.5 to 1.5 mm. The number of blades included in the impeller is in the range of 6 to 9, the input of the electric blower is in the range of 500W to 1500W, and the maximum rotation speed of the impeller is 35,000 to In the range of 50,000 revolutions, the direction of formation of each blade relative to the hub is inclined in the rotational direction at the intermediate portion compared to the inner and outer edges of the blade.

  Alternatively, the formation direction of each blade with respect to the hub is inclined in the rotational direction at the intermediate portion compared to the inner edge and outer edge of the blade, and at least one of the connection portion between the blade and the shroud and the connection portion between the blade and the hub Cover with electrodeposition or adhesive.

  Alternatively, the blade has an approximately two-dimensional shape at the inlet and the outlet, falls between the inlet and the outlet in the rotational direction, and has a crescent shape when viewed from the axial direction.

  Alternatively, the blade has a substantially two-dimensional shape at the inlet and the outlet, falls in the rotational direction at the intermediate portion between the inlet and the outlet, and further has a maximum inclination angle of 5 to 10 degrees at the intermediate portion. .

  Alternatively, a plurality of caulking projections are formed on each of the upper end portion on the blade shroud side and the lower end portion on the hub side, and caulking projections are formed on the vane so as to be substantially perpendicular to the shroud and the hub. Then, the caulking projections are inserted into holes formed in the shroud and the hub, respectively, and the vanes are fixed to the shroud and the hub by caulking.

  Alternatively, the formation direction at the inner edge of each blade with respect to the hub is inclined in the rotation direction as compared with the formation direction at the outer edge of each blade with respect to the hub, and the inclination angle of the formation direction at the inner edge of each blade with respect to the hub in the rotation direction is Greater than 45 degrees.

  Alternatively, the formation direction at the inner edge of each blade relative to the hub is inclined to the rotation direction side as compared to the formation direction at the outer edge of each blade relative to the hub, and the inclination angle to the rotation direction side of the formation direction at the outer edge of each blade relative to the hub Is greater than 0 degrees.

  According to the present invention, by matching the inlet leakage and the blade angle distribution, the separation phenomenon and the backflow phenomenon in the air flow inside the fan are suppressed, and high efficiency is achieved not only at the design point but also in the low air volume region. Can do.

  Further, according to the present invention, the assembly accuracy can be improved by optimizing the direction of the caulking projection.

  In addition, according to the present invention, since the inclination of the inner edge of each blade relative to the hub toward the rotation direction in the formation direction is greater than 45 degrees, the blade can be inclined so as to coincide with the air inflow direction. The air can be prevented from hitting the side surfaces of the blades, and the collision loss can be reduced. Further, according to the present invention, when the formation direction of the inner edge of each blade with respect to the hub is greatly inclined to the rotation direction side as compared with the formation direction of the outer edge, the formation direction of the outer edge toward the rotation direction side is increased. By making the inclination angle larger than 0 degree, it is possible to suppress the non-uniform flow of air from the shroud to the hub, that is, to suppress the non-uniform pressure distribution from the shroud to the hub. The purpose is to provide a low-efficiency electric blower and a vacuum cleaner equipped with the electric blower.

It is a typical cross-sectional view of a cleaner body. It is sectional drawing of the electric blower for vacuum cleaners. It is a block diagram of the impeller eyeball vicinity. It is a shape figure of a blade | wing. It is a figure which shows blade | wing installation angle distribution in the shroud and main plate contact surface of a blade | wing. It is a comparison figure of the efficiency of an Example and a conventional product. It is a comparison figure of the loss of an Example and a conventional product. It is a figure which shows caulking. It is a figure which shows the position of crimping. It is a figure which shows the position of crimping. It is the figure which abbreviate | omitted caulking of the intermediate position. It is another block diagram of a wing | blade. It is a shape figure of a blade | wing.

  Embodiments 1 to 5 of the present invention will be described below in detail with reference to the drawings.

  Hereinafter, an embodiment of the present invention will be described with reference to the drawings.

  First, the whole vacuum cleaner will be described with reference to FIG. The configuration of the vacuum cleaner main body 100 will be described with reference to a cross-sectional view seen from above of the vacuum cleaner main body 100 schematically shown in FIG. If the side to which the hose joint 101 of the vacuum cleaner body 100 is attached is the front side of the vacuum cleaner body 100, the vacuum cleaner body 100 includes a detachable hose joint 101 at the front end. A dust collection chamber 102 for holding the paper pack 103 is provided on the front side of the vacuum cleaner main body 100, and a motor chamber 105 for housing the electric blower 106 is provided on the rear side of the vacuum cleaner main body 100. A filter unit 104 is provided between the chamber 102 and the motor chamber 105 to prevent dust in the dust collection chamber 102 from flowing into the motor chamber 105. The dust collection chamber 102 and the motor chamber 105 communicate with each other via the filter unit 104. The dust collection chamber 102 includes a detachable paper pack 103. The opening of the paper pack 103 communicates with the hose joint 101. As dust accumulates in the paper pack 103, the paper pack 103 swells and the bottom comes into contact with the filter unit 104 on the side opposite to the opening of the paper pack 103. The motor chamber 105 includes an electric blower 106 that generates a suction force. Anti-vibration rubber 107 (anti-vibration member) for suppressing the vibration of the electric blower 106 from being transmitted to the electric vacuum cleaner main body 100 between the front both ends of the electric blower 106 and the inner wall surface on the front side of the motor chamber 105. Is provided. The vibration isolation member may be a spring instead of rubber. The electric blower 106 includes a blower inlet 108 for sucking air at the front end, and a blower outlet 109 for discharging air on the rear side. The blower inlet 108 is open to the filter unit 104. A cord reel 110 is provided on the side of the motor chamber 105 to wind and store a power cord. Wheels are provided on both sides of the rear side of the electric blower 106. Although not shown, a hose is connected to the hose joint 101, an operation pipe is connected to the hose, an extension pipe is connected to the operation pipe, and a suction tool is connected to the extension pipe. The side where the hose joint 101 exists (upstream side) is the front side of the vacuum cleaner body 100, and the opposite side is the rear side of the vacuum cleaner body 100. The direction perpendicular to the front-rear direction of the vacuum cleaner body 100 when the vacuum cleaner body 100 is viewed from above is the left-right direction of the vacuum cleaner body 100. The side means a side closer to the left side or the right side than the center of the electric vacuum cleaner main body 100 in the left-right direction.

  Next, the air flow in the vacuum cleaner main body 100 will be described. Air flowing in from the hose joint 101 enters the dust collection chamber 102. In FIG. 1, a paper pack 103 is shown as the dust collecting means, but the material of the pack is not limited. In the case of the cyclone method, a cyclone chamber (a cyclone dust collecting case) is accommodated instead of the paper pack 103. The air from which most of the dust has been removed by the paper pack 103 further passes through the filter unit 104, but fine dust is also removed here. Thereafter, the air flow flows into the motor chamber 105. The electric blower 106 is suspended in the motor chamber 105 via an anti-vibration rubber 107, and the air flowing from the blower inlet 108 is pressurized and then exhausted from the blower outlet 109.

  Next, the electric blower 106 will be described with reference to FIG. The electric blower 106 includes a blower 201 for sucking air and an electric motor 202 for driving the blower 201.

  In the electric motor 202, a rotating shaft 205 is supported on an electric motor outer shell including a housing 203 and an end bracket 204, and a rotor 206 is attached to the rotating shaft 205. A fixed portion stator 207 is arranged on the outer periphery of the rotor 206. The supply of electricity to the rotor 206 of the rotating part is transmitted by a brush 208 and a commutator 209 that contacts the brush 208.

  The blower 201 includes an impeller 210 directly connected to the rotation shaft 205, a diffuser 211 installed on the outer peripheral side of the impeller 210, and a return guide 213 arranged facing the diffuser 211 with a partition plate 212 interposed therebetween. The fan casing 214 is configured to be accommodated. The impeller 210 is substantially in contact with the sealing material 216 provided on the fan casing 214 side in the eyeball portion 215, and has a structure that prevents leakage.

  Air that has passed through the electric blower inlet 217 corresponding to the blower inlet 108 in FIG. 1 first passes through the vicinity of the eyeball 215, and then is boosted and accelerated by the impeller 210. Thereafter, the flow passes through the diffuser 211 and turns approximately 180 ° and flows into the return guide 213. In this process, the flow is decelerated and the pressure rises accordingly. The flow that has passed through the return guide 213 flows into the motor housing 203 and cools the rotor 206, the stator 207, the brush 208, the commutator 209, and the like before being exhausted. The axial direction of the rotating shaft 205 substantially coincides with the front-rear direction of the electric vacuum cleaner main body 100. A direction orthogonal to the axial direction with respect to the rotation shaft 205 is a radial direction.

  The outer diameter of the electric fan for the vacuum cleaner targeted by the present invention is in the range of about φ60 mm to φ120 mm, the height of the blade outlet is in the range of about 6 to 12 mm, and the thickness of the blade is about 0.5 to 1. In the range of .5mm, the number of blades is in the range of about 6-9, the input is in the range of about 500W to 1500W, and the maximum speed is in the range of about 35,000 to 50,000 revolutions per minute. .

Next, the structure in the vicinity of the centerpiece 300 of the electric blower of this embodiment will be described with reference to FIG. FIG. 3 is an enlarged view of the vicinity of the eyeball 215 in FIG. A sealing material 302 corresponding to the sealing material 216 in FIG. 2 is fixed via a sealing material fixing component 301 attached to a fan casing 309 corresponding to the fan casing 214 in FIG. An impeller eyeball 315 bites into the sealing material 302 to form a sealing mechanism. Although it is important that this sealing mechanism is in this position, it is not limited to this method. The vane 306 is fixed to the axially front shroud wall 304 and the axially rear hub wall 305 by caulking 317. The blade 306 is formed of a flat plate made of a material whose main component is aluminum having a substantially uniform thickness. Here, “substantially uniform” includes thickness due to deformation during processing and thermal deformation, and thickness due to surface irregularities. The shroud is constituted by a flat plate made of a material whose main component is aluminum having a substantially uniform thickness, and has an annular shape. The side wall surface of the shroud blade 306 is the shroud wall 304. As shown in FIG. 3, the outer edge (radially outermost circumference) of the shroud faces in the radial direction, and the inner edge (radially innermost circumference) of the shroud faces in the axial direction. As shown in FIG. 3, the direction is gradually changed from the radial direction to the axial direction in the vicinity of the inner edge of the shroud. The hub is also composed of a flat plate made of a material whose main component is aluminum having a substantially uniform thickness, and has a circular shape or an annular shape. A hub blade 306 side wall surface is a hub wall 305. As shown in FIG. 3, both the outer edge and the inner edge of the hub are oriented in the radial direction. Therefore, the outer edge of the shroud and the outer edge of the hub are substantially parallel and spaced apart. The blades 306, the shroud, and the hub may be an alloy containing aluminum, a metal other than aluminum (for example, iron, stainless steel, titanium), or ceramics. In general, a plurality of crimps are prepared along both the end surfaces of the blades 306 on the shroud wall 304 side and on the hub wall 305 side. However, here, attention is paid only to the shroud wall 304 side and the innermost diameter side (inner edge side). And illustrated.
The caulking 317 is preferably formed integrally with the blade 306. For example, when the blade 306 is die-cut from the flat plate, the caulking 317 can be integrally formed with the blade 306 if the caulking 317 is also die-cut together. Alternatively, the caulking 317 can be integrated with the vane 306 by cutting the vane 306 from the flat plate and cutting the caulking 317 together. The end surface on the shroud wall 304 side of the blade 306 has a shape along the shroud wall 304, and the end surface on the hub wall 305 side of the blade 306 has a shape along the hub wall 305. An impeller 303 is configured by the shroud, the hub, and a plurality of circumferential blades 306. The hub is fixed to a rotation shaft 308 corresponding to the rotation shaft 205 in FIG. 2, and as a result, the impeller 303 is fixed to the rotation shaft 308. As a result, the impeller 303 rotates with the rotation of the rotating shaft 308. The inner edge of the blade 306 protrudes forward and forms a blade leading edge 307. There is a space between the blade leading edge 307 and the rotating shaft 308, and forms a flow path. The position of the stationary portion tip 314 on the inner periphery of the fan casing 309 and the position of the blade leading edge 307 of the blade 306 do not coincide with each other, and the stationary portion leading end 314 is positioned on the front side of the blade leading edge 307 in the axial direction. A step 316 is provided. That is, there is a step in the axial direction between the fixed portion and the rotating portion. The position of the stationary part tip 314 on the inner periphery of the fan casing 309 and the position of the shroud impeller eyeball 315 do not coincide with each other, and the stationary part tip 314 is located on the inner circumference side of the impeller eyeball 315. And a radial step 310. That is, there is a step in the radial direction between the fixed portion and the rotating portion. A thick arrow 313 indicates the direction of air flow. Air enters the entrance of the eyeball portion 215 and flows into a space (flow path) formed between two circumferentially adjacent blades 306. The presence of the radial step 310 causes a leak in the flow.

  Next, the shape of the blade 400 will be described with reference to FIG. FIG. 4A is a front view of one blade 400 viewed from the front side in the axial direction. FIG. 4B is a cross-sectional view seen from the inside in the radial direction at an intermediate point in the radial direction between the inlet vicinity 403 and the outlet vicinity 404 of one blade 400. The blade 400 corresponding to the blade 306 in FIG. 3 has a substantially two-dimensional shape in the vicinity of the inlet 403 near the rotation shaft 308 and the outlet near the opposite side 404, and rotates in an intermediate portion between the inlet and the outlet. When viewed from the axial direction, the blades have a crescent shape. The entrance end of the entrance vicinity 403 is an inner edge in the radial direction and a front edge (the foremost end in the rotation direction 405) in the circumferential direction. The exit end in the vicinity of the exit 404 is an outer edge in the radial direction and a rear edge (the last end in the rotation direction 405) in the circumferential direction. That is, in the vicinity of the inlet 403 and the vicinity of the outlet 404, the position of the end surface of the blade 400 on the shroud side 401 and the position of the end surface of the hub side 402 substantially coincide with each other in the rotational direction 405, and the end surface of the blade 400 on the shroud side 401 It is located in front of the end surface of the hub side 402 in the rotation direction 405. For example, the formation direction of the blades 400 with respect to the hub wall 305 is substantially perpendicular to the entrance 403 or slightly inclined toward the rotation direction 405 side from the substantially perpendicular (about 0 degree to 1 degree). Inclination gradually toward the rotational direction 405 side rather than substantially vertical, and gradually decreases from the intermediate point to the vicinity of the exit 404, and becomes substantially vertical in the vicinity of the exit 404. Here, as shown in FIG. 4B, the forming direction refers to the end surface on the hub side 402 of the blade 400 (the front end 406 or the center line 407 or the rear end 408 in the thickness direction of the end surface) and the end surface on the shroud side 401. The direction of a straight line connecting the front end 406 or the center line 407 or the rear end 408 in the thickness direction of the end face. Since the hub wall 305 is preferably formed substantially perpendicular to the axial direction, the direction substantially perpendicular to the hub wall 305 is substantially the axial direction. It is preferable that the maximum inclination position is an intermediate point or an inner edge side (an entrance vicinity 403 side) from the intermediate point. The blade 400 is formed by bending a flat plate, and the thickness of the blade 400 is not particularly thick in the middle portion but is substantially uniform. The inclination of the end surface of the hub side 402 to the end surface of the shroud side 401 at the intermediate portion of the blade 400 may be linear or may be curved (may be warped) as shown in FIG. . Further, as shown in FIG. 4A, the blade 400 has a radius of curvature in the vicinity of the exit 404 larger than that in the vicinity of the entrance 403 and the intermediate portion, and is substantially straight in the vicinity of the exit 404. .

  Next, the blade angle distribution of the blade according to the present invention will be described with reference to FIG. In FIG. 5, an orthogonal line with respect to a straight line connecting an arbitrary position of the blade and the central axis (axial center of the rotation shaft 308) is drawn, and an angle formed by the orthogonal line and a tangent line on the outer surface of the blade is a blade attachment angle or The blade angle is “β”. The horizontal axis is the radius. As shown in FIG. 5, at the inner edge having the smallest radius, the blade angle at the inner edge of the shroud is set larger than the blade angle at the inner edge of the main plate. More specifically, when the inner diameter of the shroud is 0.397D and the inner diameter of the hub is 0.366D with respect to the outer diameter D of the blade, the blade angle at the inner edge of the shroud is set to about 24 degrees. Is set to about 21 degrees. That is, at the inner edge, the blade angle on the shroud side is slightly larger than the hub side. At the outer edge having the largest radius, the blade angle at the shroud outer edge is set substantially equal to the blade angle at the main plate outer edge, and the blade angle at the hub outer edge is also set approximately equal to the blade angle at the main plate outer edge.

  Further, as shown by the solid curve in FIG. 5, the angular distribution of the blades in contact with the hub wall increases from the inner edge to the outer edge of the hub surface, and reaches an inflection point 502 on the inner edge side of the hub. The blade angle decreases toward the outer edge and reaches the inflection point 502 on the outer edge side. Then, after passing the inflection point 502 on the outer edge side, the blade angle increases again toward the outer edge. That is, the angular distribution of the blades in contact with the hub is set to have two inflection points 502 toward the outer edge. It is possible to have one inflection point depending on the entrance condition.

  Furthermore, the blade angle distribution on the shroud side increases from the inner edge of the shroud toward the outer edge, as shown by the dashed curve in FIG. 5, and reaches the inflection point 501 on the inner edge side of the shroud. The blade angle decreases toward the outer edge and reaches an inflection point 501 on the outer edge side. Then, after passing the inflection point 501 on the outer edge side, the blade angle increases again toward the outer edge, and finally reaches substantially the same angle as the blade angle on the hub side. That is, the angular distribution of the blades in contact with the hub is set to have two inflection points toward the outer edge.

  Furthermore, the broken line curve of the blade angle distribution on the shroud side and the solid line curve of the blade angle distribution on the hub side intersect at a substantially central position in the radial direction. The shroud blade angle is larger than the hub blade angle on the inner edge side from the intersection 503, and the shroud blade angle is smaller than the hub blade angle on the outer edge side from the intersection. The intersection 503 may be closer to the inner edge than the substantially central position, or may be closer to the outer edge. The position of the intersection 503 depends on, for example, the flow velocity and the incident angle that flows into the impeller 303.

  Subsequently, FIG. 6 shows an experimental result of measuring the static pressure efficiency of the electric blower according to the above-described embodiment. The vertical axis in FIG. 6 indicates fan efficiency, and the horizontal axis indicates air volume. As shown in FIG. 6, according to the electric blower according to this embodiment described above, it can be seen that the static pressure efficiency at the design point air volume 601 is increased as compared with the conventional product. It can also be seen that the electric blower of the present embodiment achieves higher efficiency than the conventional product even in non-design point air volume other than the design point air volume 601 in a wide flow rate range excluding the large air volume range. Here, the conventional product refers to a blade in which the intermediate portion of the blade is not inclined forward in the rotation direction, that is, a substantially two-dimensional blade in the vicinity of the inlet, the intermediate portion, and the outlet of the blade.

  Furthermore, in order to investigate the effect of improving the efficiency at the design point air volume 601 for the electric blower according to this embodiment described above, a comparison of the total pressure loss distribution by numerical analysis is shown in FIG. The darker the color, the smaller the value and the less the total pressure loss. From FIG. 7, it can be seen that in this embodiment, the loss in the throat portion where the distance between the blades 400 is the narrowest and the total pressure loss in the vicinity of the blade 400 outlet 404 are reduced in this embodiment. This is due to the blade mounting angle on the hub side 402, and it can be seen that changing the blade mounting angle increases the work of the blade, reduces energy loss, and improves efficiency.

  Hereinafter, the manufacturing method of the electric blower of this invention is demonstrated.

The caulking will be described with reference to FIG. A plurality of caulking projections 805 (rivets) are respectively installed on the upper end portion (axial front side) on the shroud side and the lower end portion (axial rear side) on the hub side of the blade 804 corresponding to the blade 306 in FIG. The As described above, the caulking projection 805 is preferably formed integrally with the blade 804. A plurality of caulking holes 802 are provided in the shroud 803 and the hub 801 so as to match the position and number of the caulking projections 805 of the blades. Therefore, the relative position between the plurality of caulking holes 802 of the shroud 803 is a position along the shape of the upper end portion of the blade 804, and the relative position between the plurality of caulking holes 802 of the hub 801 is the lower end of the blade 804. It is a position along the shape of the part. The caulking hole 802 is a through hole. For example, in the case of a conventional product, the vicinity of the blade inlet, middle portion, and outlet is substantially two-dimensional. Therefore, the relative position between the plurality of caulking holes 802 of the shroud 803 and the plurality of caulking holes 802 of the hub 801. In the present embodiment, the upper end of the blade 804 is tilted to the front side in the rotational direction 405 with respect to the lower end in the intermediate portion of the blade 804, so that a plurality of crimps of the shroud 803 are caulked. The relative position between the holes 802 is a position where the intermediate hole 802 swells forward in the rotational direction 405 as compared to the relative position between the plurality of holes 802 of the hub 801. In FIG. 8, the shroud and the hub side have three caulking structures. The respective positions of the caulking projections 805 at the upper end of the blade 804 correspond to the respective positions of the caulking projections 805 at the lower end of the blade 804. By inserting the caulking projection 805 of the blade 804 into the caulking hole 802 of the shroud 803 and the hub 801 and caulking from the outside, the blade 804 is integrated with the shroud 803 and the hub 801 and assembled. The blade shape shown in FIG. 8 has a blade outer diameter D2 of 90 mm, a blade width b2 of 6.3 mm, and b2 /
It is a flat blade shape of D2 = 0.07. Here, caulking means that a caulking projection 805 is inserted into the caulking hole 802 and the caulking projection 805 protrudes through the caulking hole 802 to the opposite side by using a dedicated tool or equipment. The act of crushing. After the caulking projection 805 of the blade 804 is inserted into the caulking hole 802 of the hub 801 and caulked, and the vane 804 is fixed to the hub 801, the caulking projection 805 of the vane 804 is inserted into the caulking hole 802 of the shroud 803. It may be caulked or vice versa. Further, the caulking protrusion 805 of the blade 804 may be inserted into the caulking hole 802 of the hub 801 and the caulking hole 802 of the shroud 803 and then caulking may be performed. Next, the positional relationship between the caulking protrusion 904 corresponding to the caulking protrusion 805 in FIG. 8 and the blade 901 corresponding to the blade 804 in FIG. 8 will be described with reference to FIG. In the comparative example, as shown in FIG. 9B, when the direction of the caulking projection 904 substantially coincides with the direction of the blade 901, the caulking projection 904 is inserted obliquely with respect to the shroud 902 or the hub 903. When caulking, the blade 901 and the caulking projection 904 are likely to slide along the caulking hole corresponding to the caulking hole 802 in FIG. 8, and the distance b between the shroud 902 and the hub 903 cannot be fixed and becomes unstable. Unavoidable.

  On the other hand, in this embodiment, as shown in FIG. 9A, the caulking projection 904 and the blade 901 are caulked when the caulking projection 904 is formed substantially perpendicular to the shroud 902 and the hub 903. Therefore, the distance b between the shroud 902 and the hub 903 is stabilized, and the assembly accuracy when the shroud 902, the hub 903, and the blades 901 are assembled is improved. However, in order to obtain the effect, it is not necessary to be substantially vertical, and it is only necessary that the forming direction of the caulking projection 904 is not the same as the forming direction of the blades 901, that is, the forming direction of the caulking projection 904 is different. What is necessary is just to incline even a little in the substantially perpendicular direction with respect to the shroud 902 and the hub 903 rather than the formation direction of the blade | wing 901. FIG. Here, “substantially vertical” means that an error is included. Therefore, substantially vertical includes about plus or minus 1 degree with respect to 90 degrees.

  Compared with the conventional product, in this embodiment, the blade 901 is inclined forward in the rotational direction, particularly in the middle portion of the blade 901, so that the space between the blade 901 and the shroud wall 304 and the space between the blade 901 and the hub wall 305 are reduced. It becomes difficult to maintain airtightness. Therefore, it is preferable to coat the caulking portion 905 (connection portion) between the blade 901 and the shroud wall 304 and the caulking portion 905 (connection portion) between the blade 901 and the hub wall 305 with electrodeposition coating or an adhesive. In particular, those having a lower viscosity than the electrodeposition coating or adhesive used for conventional products are preferred. As a result, it is possible to prevent a gap from being formed in the caulking portion 905 (connection portion) between the blade 901 and the shroud wall 304 and the caulking portion 905 (connection portion) between the blade 901 and the hub wall 305, thereby suppressing air flow disturbance. And the fall of efficiency can be controlled.

  Since the basic configuration is the same as that of the first embodiment, the same elements are denoted by the same reference numerals and the description thereof is omitted.

  As shown in FIG. 10, the caulking projection 805 at the upper end of the blade 804 of Example 1 and the caulking projection 805 at the lower end opposite thereto are arranged so that their radial positions do not coincide with each other. Each of the caulking projections 805 at the upper end of the blade 804 is shifted toward the inner peripheral side by 1004 in the radial direction with respect to the caulking projection 805 at the lower end.

  As a result, the stress generated during caulking can be dispersed, the vane 804 and the caulking portion 905 are not easily crushed, and assemblability is improved.

  Since the basic configuration is the same as that of the first embodiment, the same elements are denoted by the same reference numerals and the description thereof is omitted.

  As shown in FIG. 11, in the vicinity of the inlet 403 and the vicinity of the outlet 404 of the blade 400, since the blade 400 has a substantially two-dimensional shape, caulking protrusions 805 are provided on the upper end portion and the lower end portion, respectively. In the intermediate portion 1105, since the blade has a three-dimensional shape, it is difficult to apply a force structurally, so that the caulking projection of the intermediate portion 1105 is eliminated.

  According to such a configuration, in addition to the same effects as those of the first embodiment, the number of caulking projections 805 is reduced, so that the manufacturing material can be saved and the weight can be reduced.

  If the shape of the blade viewed from the axial direction is such that the vicinity of the inlet 403 and the vicinity of the outlet 404 have a substantially two-dimensional shape, and the blade of the intermediate portion 1105 has a three-dimensional shape, the blade of the intermediate portion 1105 collapses. May be in another form. For example, as shown in FIGS. 12A and 12B, only the upper half of the blade may fall in the axial direction.

  As mentioned above, although preferred embodiment of this invention was described, it cannot be overemphasized that this invention is not limited to the said embodiment.

  Since the basic configuration is the same as that of the first embodiment, the same elements are denoted by the same reference numerals and the description thereof is omitted.

  The blade according to the first embodiment has a substantially two-dimensional shape in the vicinity of the inlet 403 and the vicinity of the outlet 404, and falls in the rotation direction 405 at the intermediate portion between the inlet vicinity 403 and the outlet vicinity 404, and reaches the maximum in the intermediate portion. The same effect as in the first embodiment can be obtained by installing the blade so that the inclination angle 1307 of the blade becomes 5 to 10 degrees, preferably about 7 degrees with respect to the axial direction 1306.

  The inflow direction of the air into the blades 400 is the inflow speed in the axial direction of air to the electric blower inlet 217 (direction substantially perpendicular to the hub wall 605) and the rotation of the blade 400 in the circumferential direction at the electric blower inlet 217. It can be obtained by a combined vector with speed (circumferential speed). Therefore, the slower the inflow rate of air into the electric blower inlet 217 in the axial direction, the higher the rotational speed in the circumferential direction of the blade 400 at the electric blower inlet 217, the more the inflow direction of air is inclined with respect to the axial direction. Thus, the air easily hits the side surface of the blade 400. However, the inflow speed of the air in the axial direction depends not only on the peripheral speed of the blade 400 but also on the opening area of the electric blower inlet 217.

  Therefore, in the sixth embodiment, the formation direction of the blades 400 with respect to the hub wall 305 is largely inclined toward the rotation direction 405 side in the vicinity of the entrance 403 (for example, 65 degrees to 70 degrees). The slope gradually decreases to the point, and gradually decreases from the intermediate point to the vicinity of the exit 404. That is, the slope is gradually reduced by the continuous angular distribution from the entrance vicinity 403 to the exit vicinity 404. It was made to incline to the rotation direction 405 side rather than substantially vertical (about 45 to 50 degrees). However, the inclination in the vicinity of the exit 404 was made smaller than that in the vicinity of the entrance 403. If the inclination angle of the blade 400 in the vicinity of the entrance 403 from the substantially vertical direction to the rotation direction 405 side is 65 degrees, the formation direction of the blade 400 with respect to the hub wall 305 is 25 degrees. If the inclination angle of the blade 400 in the vicinity of the outlet 404 from the substantially vertical direction to the rotation direction 405 side is 45 degrees, the formation direction of the blade 400 with respect to the hub wall 305 is 45 degrees. Therefore, the formation angle of each blade 400 with respect to the hub wall 305 is small at the inner edge and larger at the outer edge.

  And the formation direction in the inner edge of each blade | wing 400 with respect to the hub wall 305 inclines in the rotation direction 405 side compared with the formation direction of the outer edge of each blade | wing 400 with respect to the hub wall 305, and the inclination to the rotation direction 405 side in an inner edge. The angle is made larger than 45 degrees (for example, 65 degrees to 70 degrees), the inclination angle toward the rotation direction 405 side at the outer edge is made larger than 0 degrees (for example, 45 degrees to 50 degrees), and further The inclination is gradually reduced from the inner edge toward the outer edge. That is, the blade 400 is largely inclined toward the rotation direction 405 in the vicinity of the entrance 403, and the inclination gradually decreases toward the outer edge. Therefore, the blades 400 of the sixth embodiment are all three-dimensional from the inner edge to the outer edge.

  The inclination of the formation direction at the inner edge of each blade 400 with respect to the hub wall 305 toward the rotation direction 405 is larger than 45 degrees (for example, 65 degrees to 70 degrees), so that the blades match the air inflow direction. 400 can be inclined, air can be prevented from hitting the side surface of the blade 400, and collision loss can be reduced.

  Furthermore, when the formation direction at the inner edge of each blade 400 with respect to the hub wall 305 is greatly inclined toward the rotation direction 405, the formation direction of the outer edge of each blade 400 with respect to the hub wall 305 is substantially perpendicular to the hub wall 305. Rather than being inclined, the air flow becomes substantially uniform when viewed from a plane substantially perpendicular to the hub wall 305 (that is, from the shroud wall 304 to the hub wall 305), that is, the pressure is inclined. Distribution becomes substantially uniform and energy loss can be reduced. Since the inclination of the outer edge of each blade 400 toward the rotation direction 405 is smaller than the inclination of the inner edge of each blade 400 toward the rotation direction 405, the circumferential component of the air flow in the vicinity of the outlet 404 is changed to the vicinity of the inlet 403. Therefore, the air in the vicinity of the outlet 404 can be easily turned in the direction of about 180 °. Furthermore, by gradually reducing the inclination in the rotation direction 405 side from the inner edge to the outer edge of the blade 400, it is possible to suppress the separation of air from the wall surface of the blade 400 from the inner edge to the outer edge of the blade 400, thereby reducing energy loss. Further, since the blade 400 is formed by bending a single flat plate rather than joining an inducer formed separately from the blade 400 on the inlet side of the blade 400, a joint portion that easily causes a step is not required. The air can be prevented from peeling from the wall surface of the blade 400 from the inner edge to the outer edge of the blade 400, and energy loss can be reduced.

  Instead of gradually decreasing the slope from the entrance vicinity 403 to the intermediate point and gradually decreasing the slope from the intermediate point to the exit vicinity 404, the inclination is gradually increased from the entrance vicinity 403 to the intermediate point in the same manner as in the first embodiment. And the slope may be gradually reduced from the intermediate point to the vicinity of the exit 404.

DESCRIPTION OF SYMBOLS 100 Vacuum cleaner main body 101 Hose coupling 102 Dust collection chamber 103 Paper pack 104 Filter part 105 Motor chamber 106 Electric blower 107 Anti-vibration rubber 108 Blower inlet 109 Blower outlet 110 Code reel 111 Wheel 201 Blower 202 Electric motor 203 Housing 204 End bracket 205, 308 Rotating shaft 206 Rotor 207 Stator 208 Brush 209 Commuter 210, 303 Impeller 211 Diffuser 212 Partition plate 213 Return guide 214, 309 Fan casing 215, 300 Eyepiece portion 216, 302 Sealing material 217 Electric blower inlet 301 Sealing material fixing part 304 Shroud Wall 305 Hub wall 306, 400, 804, 901 Blade 307 Blade leading edge 310 Radial step 311 Dead water area 312 Blade leading edge upper end 313 314 Stationary end 315 Impeller eyeball 316 Axial step 317 Caulking 401 Shroud side 402 Hub side 403 Near entrance 404 Near exit 405 Rotation direction 501 Shroud side inflection point 502 Hub side inflection point 503 Intersection 601 Design point Air volume 801, 903 Hub 802 Caulking hole 803, 902 Shroud 805, 904 Caulking projection 905 Caulking part 1004 Deviation 1105 Intermediate part 1306 Axial direction 1307 Blade inclination angle

Claims (10)

An annular shroud, a hub disposed opposite the shroud, a plurality of blades disposed in a circumferential direction between the shroud and the hub, and the shroud, the hub, and the blades are rotated. In the electric blower provided with the electric part,
Each blade is formed of a flat plate,
The direction of formation of each blade with respect to the hub is inclined in the rotational direction at an intermediate portion compared to the inner edge and outer edge of the blade ,
The formation direction at the inner edge of each blade relative to the hub is substantially vertical or slightly inclined in the rotational direction than substantially vertical,
The direction of formation at the outer edge of each blade relative to the hub is substantially vertical;
The electric blower characterized in that the inclination of the blades in the direction of rotation with respect to the hub in the rotational direction gradually increases from the inner edge toward the intermediate portion and gradually decreases from the intermediate portion toward the outer edge . In the electric blower according to claim 1,
The outer diameter of the impeller is in the range of φ60 mm to φ120 mm,
The height relative to the hub at the outer edge of the blade is in the range of 6-12 mm;
The thickness of the blade is in the range of 0.5 to 1.5 mm,
The number of blades included in the impeller is in the range of 6 to 9,
The input of the electric blower is in the range of 500W-1500W,
The electric blower characterized in that the maximum rotational speed of the impeller is in the range of 35,000 to 50,000 revolutions per minute . In electric blower according to claim 2,
An electric blower characterized in that an inner edge side of the shroud is curved in the axial direction to form an air suction port . In the electric blower according to claim 1 ,
The electric blower characterized in that a maximum inclination angle in the intermediate portion is 5 degrees to 10 degrees . In the electric blower according to claim 1 ,
The electric blower characterized in that the angle of inclination of the outer edge of each blade with respect to the hub toward the rotational direction in the forming direction is greater than 0 degrees . An annular shroud that forms a suction port, a hub disposed opposite to the shroud, a plurality of blades disposed circumferentially between the shroud and the hub, the shroud, the hub, and the blade In an electric blower provided with an electric part that rotates
The blade has a substantially two-dimensional shape at the inlet and outlet, and falls between the inlet and outlet in the rotational direction,
When viewed from the axial direction, the blade has a crescent shape,
The blade has an angle of the blade in contact with the shroud wall at the inlet from the substantially central position in the radial direction is larger than the angle of the blade in contact with the hub wall at the inlet, and the angle of the blade in contact with the shroud wall at the outlet from the substantially central position in the radial direction Is smaller than the angle of the blade | wing which touches a hub wall, The electric blower characterized by the above-mentioned. In the electric blower according to claim 6,
An electric blower characterized in that the blade angle on the shroud side of the blade is larger on the inner edge side than the blade angle on the hub side and substantially equal on the outer edge side. In the electric blower according to claim 6 ,
Two inflection points in the angular distribution on the shroud side of the blade,
An electric blower having two or one inflection point in the angular distribution on the hub side of the blade . In the electric blower according to claim 1 or 6 ,
At least one of the connecting portion between the blade and the shroud and the connecting portion between the blade and the hub is covered with an electrodeposition coating or an adhesive . In a vacuum cleaner having a vacuum cleaner body including a motor chamber and an electric blower housed in the motor chamber,
The electric blower includes an annular shroud, a hub disposed opposite to the shroud, a plurality of blades disposed in a circumferential direction between the shroud and the hub, and the shroud.
And an electric part that rotates the hub and the blade,
Each blade is formed of a flat plate,
The direction of formation of each blade with respect to the hub is inclined in the rotational direction at an intermediate portion compared to the inner edge and outer edge of the blade,
The formation direction at the inner edge of each blade relative to the hub is substantially vertical or slightly inclined in the rotational direction than substantially vertical,
The direction of formation at the outer edge of each blade relative to the hub is substantially vertical;
The electric vacuum cleaner according to claim 1, wherein an inclination of each blade in a direction of rotation with respect to the hub gradually increases from an inner edge toward an intermediate portion and gradually decreases from an intermediate portion toward an outer edge .

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