TW201505598A - Household electric dust collector - Google Patents

Abstract

The invention provides a household electric dust collector which achieves improvement of suction power and enables to the maximal current to be reduced to below the upper limit value (small than 15A) of a household power socket. The household electric dust collector comprises an electric fan. The electric fan comprises a circular protective cover, a hub opposite to the protective cover, a plurality of vanes arranged between the protective cover and the hub in the peripheral direction, and an electric motor driving the protective cover, the hub and the vanes to rotate. The household electric dust collector is characterized in that the rated power consumption of the household electric dust collector is larger than 1150W and less than or equal to 1500W; current of a suction power point is larger than 13.2A; and the maximal current is less than 15A.

Description

Household vacuum cleaner

The present invention relates to a household vacuum cleaner.

For example, Japanese Laid-Open Patent Publication No. 2011-226398 (Patent Document 1) is known. After the air passing through the inlet of the electric blower corresponding to the inlet of the blower first passes through the vicinity of the center portion, the impeller is boosted and increased in speed. After the description, the airflow through the diffuser is slightly shifted to 180°, and the airflow is decelerated during the process, and the decelerated portion causes the pressure to rise.

In particular, Patent Document 1 discloses that the blades are provided at eight equal intervals in the circumferential direction, and are twisted from the center portion of the impeller toward the outer side in the radial direction in the rotational direction and the reverse rotation direction, and are twisted again in the rotational direction.

[Advanced technical literature] [Patent Literature]

[Patent Document 1] Japanese Patent Laid-Open Publication No. 2011-226398

In the conventional electric blower, there has been revealed an improvement in efficiency, and it is described that the suction work rate of the vacuum cleaner can be improved. In addition, the measurement method of the suction work rate is determined by JIS C 9108 (2009) "vacuum cleaner". The suction working rate is the maximum value of the aerodynamic dynamic curve formed by the measured value of the aerodynamic force obtained by the product of the air volume and the vacuum. In order to achieve a high suction operation rate, in addition to the efficiency of the electric blower for raising the blower as in the prior art, there is a method of increasing the power consumption of the vacuum cleaner (the power consumption of the electric blower). When the power consumption of the electric blower is increased in order to increase the suction operation rate, it is effective to increase the current of the air volume point (hereinafter, the suction operation rate point) at which the suction operation rate is obtained as shown in FIG. However, when the current at the suction operation rate is increased, the increase in the suction operation rate can be expected, but the maximum current in the operating conditions at the time of measuring the suction operation rate increases, and there is a so-called power outlet that is used in general households. The current capacity (15A) concerns.

Further, increasing the current at the suction operation rate point requires a high torque of the motor, an increase in the shaft power of the blower, or both. The efficiency of the electric blower is also reduced by the increase in the current of the motor and the increase in the shaft power of the blower, and the increase in the suction work rate is reduced.

An object of the present invention is to provide a household vacuum cleaner which has both an increase in suction operation rate and a maximum current reduction to an upper limit (less than 15 A) of a household power outlet.

Moreover, the object of the present invention is to provide an inhalation even if it is to be inhaled When the current at the operating rate is increased, the maximum current can be reduced to the upper limit of the household power outlet (less than 15A), and the efficiency of the impeller can be improved, and the household vacuum cleaner can be improved.

In order to achieve the above object, for example, a structure described in the scope of the patent application is employed.

The present invention includes a plurality of means for solving the above problems, and the household vacuum cleaner of the present invention includes an electric blower, and the electric blower includes an annular cover; and the shield is opposed to the cover a hub configured to be disposed in a circumferential direction between a plurality of blades disposed between the shroud and the hub; and an electric motor that rotates the shroud and the hub and the blade, wherein the household vacuum cleaner has a rated power consumption exceeding 1150W is below 1500W, and the current at the suction working rate is above 13.2A, and the maximum current is less than 15A.

According to the present invention, it is possible to provide a household vacuum cleaner which has both an increase in the suction operation rate and a reduction in the maximum current to the upper limit (less than 15 A) of the household power outlet.

Moreover, according to the present invention, it is possible to reduce the maximum current to the upper limit value (less than 15 A) of the household power outlet even when the current at the suction operation rate is increased, and it is also possible to improve the efficiency of the impeller. Household vacuum cleaners that increase the rate of inhalation.

100‧‧‧ vacuum cleaner body

101‧‧‧Hose connector

102‧‧‧dust room

103‧‧‧ paper bags

104‧‧‧Filter Department

105‧‧‧Motor room

106‧‧‧Electric blower

107‧‧‧Anti-vibration rubber

108‧‧‧Air blower inlet

109‧‧‧Air blower exit

110‧‧‧Wire reel

111‧‧‧ Wheels

112‧‧‧Control circuit

201‧‧‧Air blower

202‧‧‧Electric motor

203‧‧‧Shell

204‧‧‧End bracket

205‧‧‧Rotary axis

206‧‧‧Rotor

207‧‧‧ Stator

208‧‧‧carbon brush

209‧‧‧Rectifier

210, 400, 700, 900, 1100‧‧‧ impeller

211‧‧‧Diffuse wings

212‧‧‧ partition board

213‧‧‧Reflow guide

214‧‧‧Fan cover

215‧‧‧ Central Department

216‧‧‧ sealing material

217‧‧‧Electric blower inlet

218‧‧‧ bearing

300‧‧‧Changes in current and inhalation rates

402, 702, 902, 1102‧‧‧ impeller inlet

403, 703, 1103‧‧‧ leading edge

404, 1104‧‧‧ forward blades

405, 1105‧‧‧ Negative pressure surface

406, 1106‧‧‧ entrance throat width

407, 705, 903, 1107‧‧ ‧ trailing edge

408, 1108‧‧‧ pressure surface

409, 1109‧‧‧Export throat width

410, 707, 1110‧‧‧ Shield wall

411, 708, 1111‧‧‧ wheel hub

412‧‧‧ overlap

413‧‧‧The circle of the overlapping section

414‧‧‧ overlap length

415‧‧‧ Impeller exit radius

416, 704, 904‧‧‧ rotating central axis

417, 709, 909, 1112‧‧ ‧ direction of rotation

500, 800, 1000, 1200 ‧ ‧ current ratio and impeller efficiency

501, 801, 1001, 1201‧‧‧ current ratio upper limit

502, 802, 1002, 1202‧‧‧ necessary current ratio range

600‧‧‧Changes in efficiency and current and suction rate of electric blowers

706‧‧‧Wound angle

905‧‧‧ Straight line connecting the trailing edge of the blade to the central axis of rotation

906‧‧ Orthogonal line

907‧‧‧ tangent outside the blade

908‧‧‧blade exit angle

Fig. 1 is a cross-sectional view showing a mode of a cleaner body.

Fig. 2 is a cross-sectional view showing an electric blower for a vacuum cleaner.

FIG. 3 shows a change in current value when the power consumption of the cleaner is increased by the prior art.

4] (a) is a front view of the impeller of Embodiment 1 as viewed from the axial front side. (b) is a side view of the impeller of Embodiment 1 as viewed from a plane perpendicular to the rotation axis.

Fig. 5 (a) is a view showing a relationship between an overlap length ratio and a current ratio in the first embodiment. (b) is a graph showing the relationship between the overlap length ratio of Example 1 and the impeller efficiency.

Fig. 6 (a) is a view showing the relationship between the efficiency of the electric blower, the current, and the aerodynamic force with respect to the air volume of the prior art. (b) is a graph showing the relationship between the efficiency of the electric blower, the current, and the aerodynamic force with respect to the air volume of the embodiment.

Fig. 7 (a) is a front view of the embodiment 2 as seen from the axial front side. (b) is a side view of the impeller of Embodiment 2 as viewed from a plane perpendicular to the rotation axis.

Fig. 8 (a) is a view showing a relationship between a winding angle and a current ratio in the second embodiment. (b) is a view showing the relationship between the winding angle of Example 2 and the impeller efficiency.

Fig. 9 is a front view of Embodiment 3 as seen from the axial front side.

Fig. 10 (a) is a view showing a relationship between a blade exit angle and a current ratio in the third embodiment. (b) shows the blade exit angle and impeller efficiency of Example 3. Diagram of the relationship.

[Fig. 11] (a) is a front view of the impeller of Embodiment 4 as seen from the axial front side. (b) is a side view of the impeller of Embodiment 4 as viewed from a plane perpendicular to the rotation axis.

Fig. 12 (a) is a view showing the relationship between the amplification factor and the current ratio in the fourth embodiment. (b) is a graph showing the relationship between the amplification factor of Example 4 and the impeller efficiency.

Hereinafter, Embodiments 1 to 4 of the present invention will be described in detail based on the drawings.

[Example 1]

Hereinafter, an embodiment of the present invention will be described using the drawings.

First, the entire cleaner will be described with reference to Fig. 1 . The configuration of the cleaner body 100 in the cross-sectional view seen from the cleaner body 100 shown in the mode of Fig. 1 will be described. The side of the hose connector 101 of the cleaner body 100 is detachably attached to the front side of the cleaner body 100.

A dust collecting chamber 102 for holding the paper bag 103 is provided on the front side of the cleaner body 100, and a motor chamber 105 for accommodating the electric blower 106 is provided on the rear side of the cleaner body 100, and is provided between the dust collecting chamber 102 and the motor chamber 105. The dust leaks from the paper bag 103, and the filter portion 104 for the case where the dust in the dust collecting chamber 102 flows into the motor chamber 105 can be suppressed. The dust collection chamber 102 and the motor chamber 105 are in communication via the filter unit 104. Dust collection The chamber 102 is provided with a paper bag 103 that is detachable. The opening of the paper bag 103 communicates with the hose connector 101. When the dust is accumulated in the paper bag 103, the paper bag 103 is inflated, and the bottom portion on the side opposite to the opening of the paper bag 103 is brought into contact with the filter portion 104. The motor room 105 is provided with an electric blower 106 that generates an attractive force. An anti-vibration rubber 107 (anti-vibration member) for suppressing the vibration of the electric blower 106 from being transmitted to the cleaner body 100 is provided between the front end of the electric blower 106 and the wall surface on the front side of the motor chamber 105. The anti-vibration member can also use a spring instead of rubber. The electric blower 106 is provided with a blower inlet 108 for sucking air at the front end, and a blower outlet 109 for exhausting air on the side of the rear side. Moreover, the blower inlet 108 faces the opening of the filter portion 104. A wire reel 110 for winding a power supply wire and accommodating it is provided on the side of the motor chamber 105. Further, a control circuit 112 that senses the current of the electric blower and controls the operating conditions is provided. Further, wheels 111 are provided on both sides of the rear side of the cleaner body 100. Further, although not shown, a hose is connected to the hose joint 101, an operation tube is connected to the hose, an extension tube is connected to the operation tube, and an suction device is connected to the extension tube.

Next, the flow of air in the cleaner body 100 will be described. The air flowing in from the hose joint 101 enters the dust collecting chamber 102. Although the paper bag 103 is shown as a dust collecting means in FIG. 1, the material of a paper bag is not limited. On the other hand, in the case of the whirlwind mode, the whirl chamber (the cyclone type dust box) is accommodated in place of the paper bag 103. The air of the dust is removed by the paper bag 103 and then flows into the motor chamber 105. The electric blower 106 is suspended in the motor chamber 105 via the anti-vibration rubber 107, and the air that has flowed in from the blower inlet 108 is pressurized, and then exhausted from the blower outlet 109. Although not shown, the cleaner body 100 may be omitted. The exhaust port is exhausted to the outside.

Next, the electric blower 106 will be described with reference to Fig. 2 . The electric blower 106 is composed of a blower 201 for sucking air and a motor 202 for driving the blower 201.

The motor 202 is a motor casing formed of a casing 203 and an end bracket 204, and supports a rotating shaft 205 via a bearing 218, and a rotor 206 is attached to the rotating shaft 205. A stator 207 having a fixed portion is disposed on the outer circumference of the rotor 206. The electrical supply to the rotor 206 of the rotating portion is transmitted by the carbon brush 208 and the rectifier 209 in contact therewith.

The blower 201 has a structure in which an impeller 210 that is directly coupled to the rotating shaft 205, a diffusing blade 211 that is provided on the outer peripheral side of the impeller 210, and a partitioning plate 212 that is sandwiched between the diffusing blades 211 are housed in the fan casing 214. The opposite return guide 213. The impeller 210 is in contact with the seal member 216 provided in the fan cover 214 at the center portion 215, and has a structure for preventing air leakage, that is, preventing circulation.

The air passing through the electric blower inlet 217 corresponding to the blower inlet 108 of Fig. 1 is boosted and accelerated by the impeller 210 after passing through the vicinity of the center portion 215. Thereafter, the airflow passing through the diffusion vane 211 is slightly turned toward the reflux guide 213 by 180°, but the airflow is decelerated during the process, and the decelerating portion causes the pressure to rise. The airflow passing through the return guide 213 flows into the casing 203 of the motor 202, and the rotor 206, the stator 207, the carbon brush 208, the rectifier 209, and the like are cooled and exhausted. The axial direction of the rotating shaft 205 slightly coincides with the front-rear direction of the cleaner body 100. The direction orthogonal to the axial direction is the radial direction with reference to the rotation axis 205.

The outer diameter of the impeller of the electric blower used for the household vacuum cleaner of the present invention is approximately 60mm~ In the range of 120mm, the blade exit height is about 6~12mm, the blade thickness is about 0.5~1.5mm, the number of blades is about 6~13, and the maximum rotation is about 35,000~50,000 rpm. range. Moreover, the rated power consumption of the household vacuum cleaner is approximately in the range of more than 1150 W in the range of 1500 W or less.

Next, the shape of the impeller 400 will be described using FIG. Here, the impeller 210 in FIG. 2 will be described as the impeller 400. Fig. 4 (a) is a front view of the impeller 400 as viewed from the axial front side. 4(b) is a side view of the impeller 400 as viewed from a plane perpendicular to the rotation axis. In addition, FIG. 4 is a view showing the shield wall 410 in a semi-transparent shape in order to easily view the shape of the blade 401. The blade 401 is provided in a circumferential direction at equal intervals between the shroud wall 410 and the hub wall 411, and has a blade shape that retreats from the impeller inlet 402 toward the outer side in the radial direction. Further, although the blade of Fig. 4 shows a blade having a shape of a slightly second dimension in the axial direction, it may be a shape that can be twisted in the radial direction or a blade of a three-dimensional shape. Further, when the blade is subjected to press working, when the hub wall and the shroud wall are provided, it is easy to form the riveting. Further, in the embodiment of the present embodiment, an impeller having a shroud wall is described, but an unfolded impeller having no shroud wall may be used.

Here, the leading edge (the innermost edge of the blade) 403 of the blade shown in FIG. 4 faces the negative pressure surface 405 of the blade (the blade of the forward position) 404 on the side of the rotation direction (the side that retreats toward the rotation direction of the blade) The line formed by the shortest distance of the wall is the inlet throat width a ₁₀ 406, and the blade facing the side opposite to the reverse rotation direction by the trailing edge 407 (the outermost edge of the blade) of the advancing blade 404 (retracted position) The line formed by the shortest distance of the pressure surface 408 of the blade 401 (the wall on the side advancing toward the rotation direction of the blade) serves as the outlet throat width a ₂₀ 409. The shape of the pressure surface 408 that connects the blade 401 to the inner wall of the shroud wall 410, and the portion of the vane 401 that overlaps the vane 404 formed by the shape of the negative pressure surface 405 where the advancing position vane 404 is connected to the inner wall of the shroud wall 410 It is defined as an overlap 412. Further, when the blades 401 and 404 are not provided as the inner wall of the shroud wall 410, a shape in which the end portion on the inner wall side of the shroud of the blade is projected to the front surface seen from the axial direction is formed. Further, the overlapping portion 412 is projected into the shape formed by the front surface viewed from the axial direction, and the shape of the inlet throat width a ₁₀ 406 and the outlet throat width a ₂₀ 409 are drawn along the overlapping portion 412. The tangent circle 413 and the length 414 passing through the center of each circle is defined as the overlap length L.

Fig. 5 shows the current of the overlap length L414 and the blade exit radius R ₂ 415 as the overlap length ratio at the overlap length ratio L/R ₂ and the current I _d and the maximum current I _max at the suction operation rate of the household vacuum cleaner. A graph of the relationship (impact) of the ratio I _max /I _d , the relationship between the overlap length ratio and the impeller efficiency (impact). Further, the maximum current is the maximum value of the current measured by the measurement method of the suction operation rate prescribed by JIS C 9108 (2009) "vacuum cleaner". Fig. 5(a) shows the overlap length ratio on the horizontal axis and the current ratio on the vertical axis. Fig. 5(b) shows the overlap length ratio on the horizontal axis and the impeller efficiency in the suction operation rate point on the vertical axis on the vertical axis. the result of. Further, the maximum current may be set to less than 15 A, or the current ratio at which the current at the suction operation rate is 13.2 A or more may be 1.136 or less. That is, when the current ratio is larger than 1.136, the maximum current becomes 15A or more.

As can be seen from Fig. 5(a), the overlap length ratio 501 satisfying the current ratio of 1.136 or less is 0.96 or more. On the other hand, the operation control of the vacuum cleaner detects the current of the motor in order to grasp the amount of dust collected by the garbage. In the method of detecting the current, when the current ratio shown in FIG. 5(a) is 1, there is no difference in the current value of the motor due to the dust collection amount of the garbage, and the control becomes difficult. That is, since the current ratio is 1.136 or less, since the range 502 is larger than 1, the operating state of the air volume can be detected, and the operation control of the cleaner can be performed. Therefore, it is necessary that the range of the overlap length ratio shown in FIG. 5(a) is 0.96 or more and less than 1.15. Furthermore, the optimum range of the overlap length ratio will be described using FIG. 5(b). It can be seen that the efficiency of the impeller having an overlap length ratio of 0.96 or more and less than 1.15 as shown in Fig. 5(a) is higher than that of the impeller when the overlap length ratio is 0.9. The overlap length ratio is in the range of 0.96 or more and less than 1.15. In particular, it is found that the efficiency of the impeller is the highest when the overlap length is about 1.1.

The overlap length indicates the flow path length of the blade. Therefore, when the overlap length is short, the blade flow path area will be sharply expanded and the loss due to peeling will increase. When the overlapping length is long, the flow path between the blades becomes long, so that the friction loss becomes large and the efficiency is lowered. Therefore, in the embodiment of the present embodiment, in consideration of the ratio to the impeller exit radius R ₂ , the efficiency of the overlap length ratio L/R ₂ is 0.96 or more and less than 1.15. In particular, it is more preferable that the overlap length L is in the vicinity of L/R ₂ =1.1 which is larger than the impeller exit radius R ₂ , and the sum of the loss due to the peeling and the friction loss is minimized.

Next, Fig. 6 shows a comparison between the prior art and the electric blower efficiency, current, and suction operation rate of the present embodiment. Fig. 6(a) is a view showing changes in the characteristics of the electric blower efficiency, the current, and the aerodynamic force in the prior art with respect to the increase in the amount of electric power consumption; Fig. 6(b) shows the increase in power consumption with respect to the present embodiment. The change in the air blower efficiency, current, and aerodynamic power characteristics of the air volume at the time.

The prior art shows that the overlap length of the impeller is smaller than the optimum range of the present invention. Therefore, it is conceivable that the current ratio shown in Fig. 5(a) of the present invention is 1.136 or more. In other words, when the current of the electric blower is increased in order to increase the suction operation rate, the suction operation rate can be expected to be improved. However, it is conceivable that the current at the air flow point that becomes the maximum current is 15 A or more. Further, in the prior art, since the overlap length of the impeller is smaller than the optimum range of the present invention, since the impeller efficiency cannot be increased to compensate for the decrease in the efficiency of the motor due to the increase in the current, there is a concern that the efficiency of the electric blower is lowered. The increase in the inhalation rate is small.

On the other hand, as shown in the embodiment, the overlap length ratio of the impeller is used as the optimum range, and the maximum current can be suppressed to less than 15 A, and the efficiency of the impeller can also be improved, so that the electric blower of the suction operation rate can be improved. Efficiency, and can increase the amount of increase in the suction work rate. Thereby, the maximum current can be reduced to less than 15 A, and a household vacuum cleaner equipped with an electric blower that is likely to increase the suction operation rate can be obtained.

Further, the air volume at the suction operation rate point is defined as Q _d , and the air volume at the operation condition of the maximum current is defined as Q _max , since the air volume Q _d obtained at the suction operation rate point in the present embodiment is about 1.9 m ³ /min, the maximum The air volume Q _{max is} about 3m ³ /min, the current I _d of the suction working rate point is 13.2A, and the maximum current I _max is less than 15A, so the current gradient a=(I _max -I _d )/(Q _max -Q _d ) It became about 1.63. In other words, the current gradient a that satisfies the optimum range of the current ratio and the overlap length ratio (0.96 or more and less than 1.15) shown in the present embodiment may be 1.63 or less.

Moreover, the same effect is obtained even in different electrical environments. For example, when the suction operation rate of the vacuum cleaner using the power consumption voltage of 110 V is used, there is a problem that the maximum current is reduced in addition to the fact that the current upper limit value of the power supply line is less than 15. Therefore, the maximum current is not increased, and the current at the suction operation rate is increased to increase the suction operation rate. Therefore, it is effective to set the overlap length ratio of the impeller to 0.96 or more and less than 1.15 as shown in the present invention. If it is provided in the optimum range of the present invention, even if a vacuum cleaner having a voltage of 110 V is used, the maximum current can be suppressed, and the efficiency of the impeller can be improved, so that the efficiency of the impeller of the electric blower at the suction operation rate can be increased and can be increased. The amount of increase in inhalation work rate.

[Embodiment 2]

Since the same configurations as those of the first embodiment are given, the same reference numerals will be given to the same elements, and the description thereof will be omitted.

Next, the shape of the impeller 700 will be described using FIG. Here, the impeller 210 in FIG. 2 will be described as the impeller 700. Fig. 7(a) is a front view of the impeller 700 as viewed from the axial front side. Fig. 7(b) is a side view of the impeller 700 as seen from a plane perpendicular to the rotation axis. In addition, FIG. 7 is a translucent shield wall 707 for easy viewing of the blade shape. By. The blades 701 are provided at eight equal intervals in the circumferential direction, and have a blade shape that retreats from the impeller inlet 702 toward the outer side in the radial direction to the rotational direction. Further, although the blade of Fig. 7 shows a blade having a shape of a slightly second dimension in the axial direction, it may be a shape that can be twisted in the radial direction or a blade of a three-dimensional shape. Further, when the blade is subjected to press working, when the hub wall and the shroud wall are provided, it is easy to form the riveting. Further, in the embodiment of the present embodiment, an impeller having a shroud wall is described, but an unfolded impeller having no shroud wall may be used.

Further, the leading edge 703 (the innermost edge of the blade) of the blade 701 shown in FIG. 7 and the center of the rotating shaft 704; and the trailing edge 705 (the outermost edge of the blade) of the connecting blade 701 and the center of the rotating shaft are connected. The angle formed by the lines of 704 is defined as the winding angle 706. Further, the winding angle 706 shown in FIG. 7 is represented by a blade shape connected to the inner wall of the shroud wall 707, but when it is a twisted blade or a three-dimensional blade, it serves as an inner wall connecting the shroud wall 707. Side, the winding angle 706 of any of the larger sides of the side of the hub wall 708.

Fig. 8 shows the influence of the current ratio I _max /I _d of the current I _d and the maximum current I _max at the suction operation rate of the household vacuum cleaner at the winding angle, and the impeller efficiency. Fig. 8(a) shows the winding angle on the horizontal axis and the current ratio on the vertical axis. Fig. 8(b) shows the winding angle on the horizontal axis and the impeller efficiency in the calculation of the suction operation rate using the airflow analysis on the vertical axis. the result of. The current ratio of the maximum current is less than 15 A, and the current at the suction operation rate is 13.2 A or more, which is 1.136 or less. That is, when the current ratio is larger than 1.136, the maximum current becomes 15A or more.

As can be seen from Fig. 8(a), the winding angle 801 satisfying the current ratio of 1.136 or less is 115 or more. On the other hand, the operation control of the vacuum cleaner is to detect the current of the motor in order to grasp the amount of dust collected by the garbage. In the method of detecting the current, when the current ratio shown in FIG. 8(a) is 1, there is no difference in the current value of the motor due to the dust collection amount of the garbage, and the control becomes difficult. In other words, since the current ratio is 1.136 or less and the range 802 is larger than 1, the operational state of the air volume can be detected, and the operation control of the cleaner can be performed. Therefore, it is necessary that the range of the winding angle shown in Fig. 8(a) is 115° or more and less than 128°. Furthermore, the optimum range with respect to the winding angle will be described using FIG. 8(b). It can be seen that the efficiency of the impeller in the range of the winding angle of 115° or more and less than 128° shown in Fig. 8(a) is higher than the efficiency of the impeller at the winding angle of 110°. It can be seen that in the range of the winding angle of 115° or more and less than 128°, it is particularly found that the winding angle is about 123° and the efficiency is the highest. Further, the overlap length ratio shown in FIG. 4 is set to 0.96 or more, and when the blade shape is formed in the optimum range of the winding angle, the efficiency of the high impeller can be maintained.

The winding angle 706 has an effect on the inlet throat width a ₁₀ of the overlap. If the winding angle 706 is increased, the inlet throat width a _{10 of the} overlap becomes smaller, and the blade inlet area defined by the product of the inlet throat width a ₁₀ and the blade height becomes smaller, and the air flow from the impeller inlet 702 is reduced. The shrinkage loss occurs, and the friction loss increases because of the high speed. Conversely, if the winding angle 706 is reduced, the blade inlet area becomes large, and peeling occurs at the blade inlet to lower the impeller efficiency.

Therefore, in the embodiment of the present embodiment, the winding angle θ is set to be 115° or more and less than 128°, and the impeller efficiency is the highest. especially, It is more preferable that the sum of the friction loss in the vicinity of the winding angle θ at around 123° and the loss due to the peeling is minimized.

Further, when the outlet throat portion of the fixed overlapping portion has a width a ₂₀ , if the winding angle 706 is increased, the inlet throat width a _{10 of} the overlapping portion becomes small. Therefore, the flow path of the overlapping portion is enlarged, and the peeling occurs to cause a loss. Conversely, if the winding angle 706 is reduced, the inlet throat width a _{10 of} the overlapping portion becomes larger. Therefore, the flow path of the overlapping portion is too small, the effect of the pressure increase due to the deceleration of the air flow is small, and the impeller efficiency is lowered.

Therefore, in the embodiment of the present embodiment, the winding angle θ is set to be 115° or more and less than 128°, and the impeller efficiency is the highest. In particular, it is more preferable that the winding angle θ is minimized by the peeling in the vicinity of 123°, and the effect of increasing the pressure due to the deceleration can be maximized.

Further, the air volume at the suction operation rate point is defined as Q _d , and the air volume at the operation condition of the maximum current is defined as Q _max , since the air volume Q _d obtained at the suction operation rate point in the present embodiment is about 1.9 m ³ /min, the maximum The air volume Q _{max is} about 3m ³ /min, the current I _d of the suction working rate point is 13.2A, and the maximum current I _max is less than 15A, so the current gradient a=(I _max -I _d )/(Q _max -Q _d ) It became about 1.63. In other words, the current gradient a that satisfies the optimum range of the current ratio and the winding angle (115° or more and less than 128°) shown in the present embodiment may be set to 1.63 or less.

According to the above, as shown in the embodiment, if the winding angle of the impeller is set to 115° or more and less than 128°, the maximum current can be reduced to less than 15A, and the efficiency of the impeller can be improved, so that the suction working rate is improved. The efficiency of the electric blower is possible, and the increase in the suction work rate can be increased. the amount. Thereby, the maximum current can be reduced to less than 15 A, and a household vacuum cleaner equipped with an electric blower that is likely to increase the suction operation rate can be obtained.

Moreover, the same effect is obtained even in different electrical environments. For example, when the suction operation rate of the vacuum cleaner using the power consumption voltage of 110 V is increased, there is a problem that the maximum current is reduced in addition to the problem that the current upper limit value of the power supply line is less than 15 A. Therefore, it is effective to increase the current of the suction operation rate to increase the suction operation rate without increasing the maximum current, and it is effective to set the winding angle of the impeller to 115° or more and less than 128° as shown in the present invention. If it is provided in the optimum range of the present invention, even if a vacuum cleaner using a voltage of 110 V is used, the maximum current can be suppressed, and the efficiency of the impeller can be improved, so that the efficiency of the impeller of the electric blower at the suction operation rate can be improved, and Increase the amount of increase in the suction work rate.

[Example 3]

Since the same configurations as those of the first embodiment are given, the same reference numerals will be given to the same elements, and the description thereof will be omitted.

Next, the shape of the impeller 900 will be described using FIG. Here, the impeller 210 in FIG. 2 will be described as the impeller 900. Figure 9 is a front elevational view of the impeller 900 as viewed from the axial front side. In addition, FIG. 9 is a panel which is shown in a translucent shape in order to make it easy to see a blade shape. The blade 901 has eight blade shapes which are provided at equal intervals in the circumferential direction, and has a blade shape which retreats from the impeller inlet 902 toward the outer side in the radial direction toward the rotational direction. Further, although the blade of Fig. 9 shows a blade having a shape of a second dimension in the axial direction, it may have a shape that can be twisted in the radial direction or a blade of a three-dimensional shape. Also, on the plate When the blade is pressed, when the hub wall and the shroud wall are provided, the riveting can be easily performed. Further, in the embodiment of the present embodiment, an impeller having a shroud wall is described, but an unfolded impeller having no shroud wall may be used.

Here, with respect to the straight line 905 connecting the trailing edge 903 of the blade 901 and the rotation shaft center 904 shown in FIG. 9, the orthogonal line 906 passing through the outer edge portion of the blade is pulled out, and the pressure at the outer edge portion of the blade is extracted. The angle 908 formed by the tangent 907 of the face serves as the blade exit angle β ₂ . In addition, when the tapered portion, the R portion, and the like are provided on the outer edge portion of the blade, the blade exit angle of the outermost edge portion of the outermost diameter other than the portion may be β ₂ .

Fig. 10 is a view showing the influence of the current ratio I _max /I _d of the current I _d and the maximum current I _max at the suction operation rate of the household vacuum cleaner at the blade exit angle, and the impeller efficiency. Fig. 10(a) shows the blade exit angle on the horizontal axis and the current ratio on the vertical axis. Fig. 10(b) shows the blade exit angle on the horizontal axis and the impeller at the suction operation rate on the vertical axis. The result of efficiency. Further, the maximum current may be set to less than 15 A, or the current ratio at which the current at the suction operation rate is 13.2 A or more may be 1.136 or less. That is, when the current ratio is larger than 1.136, the maximum current becomes 15A or more.

From Fig. 10(a), it is understood that the blade outlet angle β ₂ 1001 whose current ratio satisfies 1.136 or less is 27° or more. On the other hand, the operation control of the vacuum cleaner is to grasp the amount of dust collected by the garbage and to detect the current of the motor. In the method of detecting the current, when the current ratio shown in FIG. 10(a) is 1, the current value of the motor does not vary due to the amount of dust collected, and the control becomes difficult. In other words, since the current ratio is 1.136 or less and the range 1002 is larger than 1, the operational state of the air volume can be detected, and the operation control of the cleaner can be performed. Therefore, the range of the blade exit angle shown in Fig. 10(a) must be larger than 16° by 27° or less. Furthermore, the optimum range with respect to the blade exit angle is explained using FIG. 10(b). It can be seen that the blade exit angle shown in Fig. 10(a) can maintain a high impeller efficiency in the range of 16° or more and 27° or less. In particular, it can be seen that the effect of the blade exit angle of about 20° is the highest.

The blade exit angle is related to the impeller exit velocity. Further, peeling occurs at the blade outlet due to the flow of the pressure from the pressure surface of the blade to the negative pressure surface. When the blade exit angle is increased, the impeller exit speed becomes large, and the mixing loss at the blade outlet due to the collision with the airflow flowing out from the other blades increases. Conversely, when the blade exit angle is reduced, the impeller exit speed is reduced, but the peeling occurring at the blade outlet portion is increased, the remixing loss is increased, and the efficiency is lowered. Therefore, in the embodiment of the present embodiment, the blade exit angle β _{2 of the} impeller efficiency is the highest between 27° and 27° or more. In particular, it is more preferable that the mixing loss of the blade exit angle β ₂ in the vicinity of 20° is minimized.

In the description of the prior art, the blade exit angle on the shroud wall side is about 35°, and the vane outlet side vane exit angle is about 20°. Although the shaft power of the impeller is dominated by the one having a large blade exit angle, the blade exit angle of the shroud wall side and the hub wall side is about 27.5°, which is about the best range of the present embodiment. . Moreover, the average value of the blade exit angle is about 27.5°, and it is conceivable that the impeller efficiency is compared with The blade exit angle is 20‧ small. Further, when the blade shape is a three-dimensional shape, the blade exit angle may be one of the angles on the shroud wall side and the hub wall side, or the average value of both may be set in the range of the present embodiment.

Further, the air volume at the suction operation rate point is defined as Q _d , and the air volume at the operation condition of the maximum current is defined as Q _max , since the air volume Q _d obtained at the suction operation rate point in the present embodiment is about 1.9 m ³ /min, the maximum The air volume Q _{max is} about 3m ³ /min, the current I _d of the suction working rate point is 13.2A, and the maximum current I _max is less than 15A, so the current gradient a=(I _max -I _d )/(Q _max -Q _d ) It became about 1.63. In other words, the current gradient a that satisfies the optimum range of the current ratio and the blade exit angle shown in the present embodiment (27° or more larger than 16°) may be set to 1.63 or less.

According to the above, as shown in the embodiment, the blade outlet angle of the impeller is set to be 16° or more and 27° or less, and the maximum current can be reduced to less than 15 A, and the efficiency of the impeller can be improved, so that the electric power of the suction operation rate is increased. The efficiency of the blower is made possible, and the increase in the suction work rate can be increased. Thereby, the maximum current can be reduced to less than 15 A, and a household vacuum cleaner equipped with an electric blower that is likely to increase the suction operation rate can be obtained.

Moreover, the same effect is obtained even in different electrical environments. For example, when the suction operation rate of the vacuum cleaner using the power consumption voltage of 110 V is used, there is a problem that the maximum current is reduced in addition to the current upper limit value 15A of the power supply line. Therefore, the maximum current is not increased, and the current at the suction operation rate is increased to increase the suction operation rate. As shown in the present invention, the blade exit angle of the impeller is set to be 16 or more and 27 or less. effective. If it is provided in the optimum range of the present invention, even if a vacuum cleaner having a voltage of 110 V is used, the maximum current can be suppressed, and the efficiency of the impeller can be improved, so that the efficiency of the electric blower at the suction operation rate can be improved and can be increased. The amount of increase in inhalation work rate.

[Example 4]

Since the same configurations as those of the first embodiment are given, the same reference numerals will be given to the same elements, and the description thereof will be omitted.

Next, the shape of the impeller 1100 will be described using FIG. Here, the impeller 210 in FIG. 2 will be described as the impeller 1100. Fig. 11 (a) is a front view of the impeller 1100 as viewed from the axial front side. Fig. 11 (b) is a side view of the impeller 1100 as seen from a plane perpendicular to the rotation axis. In addition, FIG. 11 is a view showing the shield wall 1110 in a semi-transparent shape in order to easily view the blade shape. The blades 1101 are provided in eight blades at equal intervals in the circumferential direction, and have a blade shape that retreats from the impeller inlet 1102 toward the outer side in the radial direction to the rotational direction. Further, although the blade of Fig. 11 shows a blade having a slightly second-order axial shape, it may have a shape that can be twisted in the radial direction or a blade of a three-dimensional shape. Further, when the blade is subjected to press working, when the hub wall and the shroud wall are provided, it is easy to form the riveting. Further, in the embodiment of the present embodiment, an impeller having a shroud wall is described, but an unfolded impeller having no shroud wall may be used.

Here, in the blade 1101 shown in FIG. 11, the negative pressure of the blade (the blade at the forward position) 1104 of the leading edge (the innermost edge of the blade) 1103 of the blade 1101 shown in FIG. The line formed by the shortest distance of the face 1105 (the wall facing the side in which the blade rotates in the direction of rotation) is defined as the inlet throat width a ₁₀ 1106 and the trailing edge 1107 (the outermost edge of the blade) to be advanced by the blade 1104. A line formed by the shortest distance toward the pressure surface 1108 (the wall surface on the side advancing toward the rotation direction of the blade) of the blade (the blade at the retracted position) 1101 on the side opposite to the reverse rotation direction side is defined as the outlet throat width a ₂₀ 1109. Further, when the blades 1101 and 1104 are not provided with the inner wall of the shroud wall 1110, they are projected as projections on the front surface viewed from the axial direction.

Figure 12 is the current I _d and the maximum current I _max of the suction working rate point of the household vacuum cleaner with the outlet throat width a ₂₀ and the inlet throat width a ₁₀ as the magnification a ₂₀ /a ₁₀ . The current ratio I _max /I _d and the effect on the impeller efficiency. 12(a), the horizontal axis represents the amplification factor, and the vertical axis represents the current ratio. FIG. 12(b) shows the amplification factor on the horizontal axis, and the vertical axis represents the result of calculating the impeller efficiency at the suction operation rate point by using the airflow analysis. Further, the maximum current may be set to less than 15 A, or the current ratio at which the current at the suction operation rate becomes 13.2 A or more may be 1.136 or less. That is, when the current ratio is larger than 1.136, the maximum current becomes 15A or more.

As can be seen from Fig. 12(a), the amplification factor 1201 satisfying the current ratio of 1.136 or less is 1.45 or more. On the other hand, the operation control of the vacuum cleaner is to detect the current of the motor in order to grasp the amount of dust collected by the garbage. In the method of detecting the current, when the current ratio shown in FIG. 12(a) is 1, the current value of the motor is not different due to the amount of garbage collected, and the control becomes difficult. That is, the current ratio is 1.136 or less, and since it has a range of 1202 larger than 1, it is possible to detect the operating state of the air volume, and it is possible to enter The operation control of the vacuum cleaner. Therefore, the range of the magnification shown in FIG. 12(a) is necessary to be 1.06 or more and 1.45 or less. Furthermore, the optimum range regarding the magnification is explained using FIG. 12(b). It can be seen that the amplification factor shown in Fig. 12(a) can maintain a high impeller efficiency in the range of 1.06 or more and 1.45 or less. In particular, it is understood that the amplification factor is the highest at about 1.2.

The magnification indicates a change in the flow path area of the overlapping portion. Therefore, when the magnification is large, the flow path area between the blades is rapidly increased, and the loss due to the peeling is increased. Conversely, when the magnification is small, the friction loss of the flow path between the blades becomes large and the efficiency is lowered. Therefore, in the embodiment of the present embodiment, the amplification factor a ₂₀ /a ₁₀ is the most efficient between 1.06 and 1.45. In particular, it is more preferable that the ratio of the loss and the friction loss caused by the peeling of the magnification a ₂₀ /a ₁₀ in the vicinity of 1.2 is the smallest.

Further, the air volume at the suction operation rate point is defined as Q _d , and the air volume at the operation condition of the maximum current is defined as Q _max , since the air volume Q _d obtained at the suction operation rate point in the present embodiment is about 1.9 m ³ /min, the maximum The air volume Q _{max is} about 3m ³ /min, the current I _d of the suction working rate point is 13.2A, and the maximum current I _max is less than 15A, so the current gradient a=(I _max -I _d )/(Q _max -Q _d ) It became about 1.63. In other words, the current gradient a that satisfies the optimum range of the current ratio and the amplification factor (1.06 or more and 1.45 or less) shown in the present embodiment may be set to 1.63 or less.

According to the above, as shown in the embodiment, the expansion ratio of the impeller is set to 1.06 or more and 1.45 or less, and the maximum current can be reduced to less than 15 A, and the efficiency of the impeller can be improved, so that the efficiency of the electric blower at the suction operation rate is improved. It is possible and can increase the suction rate the amount. Thereby, the maximum current can be reduced to less than 15 A, and a household vacuum cleaner equipped with an electric blower that is likely to increase the suction operation rate can be obtained.

Moreover, the same effect is obtained even in different electrical environments. For example, when the suction operation rate of the vacuum cleaner using the power consumption voltage of 110 V is used, there is a problem that the maximum current is reduced in addition to the current upper limit value 15A of the power supply line. Therefore, it is effective to increase the suction current rate by increasing the current at the suction operation rate point without increasing the maximum current, and it is effective to set the amplification factor of the impeller to 1.06 or more and 1.45 or less as shown in the present invention. If it is provided in the optimum range of the present invention, even if a vacuum cleaner having a voltage of 110 V is used, the maximum current can be suppressed, and the efficiency of the impeller can be improved, so that the efficiency of the electric blower at the suction operation rate can be improved, and the suction operation can be increased. The amount of increase in the rate.

Claims (6)

A household vacuum cleaner is a household vacuum cleaner having an electric blower, and the electric blower includes: a ring-shaped shroud; a hub that is disposed to face the shroud; and the plurality of shrouds are disposed in the circumferential direction in the shroud a blade between the hub and the rotor; and an electric motor for rotating the shroud and the hub and the blade, wherein the household vacuum cleaner has a rated power consumption exceeding 1150 W at 1500 W or less, and the current at the suction operation rate is 13.2. Above A, and the maximum current is less than 15A. A household vacuum cleaner is a household vacuum cleaner having an electric blower, and the electric blower includes: a ring-shaped shroud; a hub that is disposed to face the shroud; and the plurality of shrouds are disposed in the circumferential direction in the shroud And a motor for rotating the shroud and the hub and the blade, wherein the household vacuum cleaner has a rated power consumption of more than 1150 W at 1500 W or less, and a current I _d at a suction operation rate point The ratio I _max /I _d to the maximum current I _max is 1.136 or less. The household vacuum cleaner according to claim 1 or 2, wherein the blade has an overlap length L of an overlapping portion formed between adjacent blades and an overlap length ratio L with an impeller exit radius R ₂ /R ₂ forms a shape of 0.96 or more and less than 1.15. Such as the household vacuum cleaner of claim 1 or 2, wherein The blade is a line having a leading edge (the innermost edge of the blade) that connects the impeller and a center of the rotating shaft; and an angle (winding angle) formed by a line connecting the trailing edge (the outermost edge of the blade) and the central axis of rotation is A shape of 115° or more and less than 128°. The household vacuum cleaner according to claim 1 or 2, wherein the blade has an orthogonal line drawn through a straight line passing through the outer edge portion of the blade with respect to a line connecting the outer edge portion of the blade and the center of the rotation axis. The blade exit angle of the angle formed by the tangent to the pressure surface located at the outer edge portion of the blade is formed into a blade shape of 16° or more and 27° or less. The household vacuum cleaner according to the first or second aspect of the invention, wherein the blade has a negative blade (a blade at a forward position) facing the side of the rotation direction from the leading edge of the blade (the innermost edge of the blade) The inlet throat of the line formed by the shortest distance of the pressing surface (the wall facing the direction of rotation of the blade) has a width a ₁₀ , and the trailing edge (the outermost edge of the blade) from the forward blade toward the reverse rotation direction side The pressure surface of the next blade (the blade in the retracted position) (the wall on the side advancing toward the rotation direction of the blade) is formed by the line of the shortest distance as the magnification of the outlet throat width a ₂₀ a ₂₀ /a ₁₀ at 1.06 Above the blade shape of 1.45 or less.