JP2009062953A - Multi-blade impeller and multi-blade blower - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a multi-blade impeller and a multi-blade blower capable of reducing noise when applying high static pressure, without reducing the air volume when applying low static pressure. <P>SOLUTION: The multi-blade impeller 8 and the multi-blade blower 1 can be provided such that the ratio (hereinafter referred to as the inner-outer diameter ratio) of a main plate side blade inner diameter D1b and a blade outer diameter D2 of a blade 13 is set to 0.7-0.8, the inner-outer diameter ratio in a blade tip part 14 is set to 0.8-0.9, the number Z of blades 13 is set to Z=(π×D2)/(t×a), 4.5<a<6.0 (here, t : the blade average thickness, and a : a constant) is satisfied, and thereby, a flow between the blades 13 can be smoothed since the area of the blades 13 is increased and an interval between the blades 13 can be properly set, and the noise can be reduced by restraining separation of the flow when applying the high static pressure, and reduction in the air volume can be restrained even when a suction orifice diameter Do is large and the low static pressure is applied. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to a multi-blade impeller and a multi-blade fan used in, for example, a ventilation blower or an air conditioner.

  In recent years, ventilation and air-conditioning equipment and air-conditioning equipment have been increasingly used in situations where high external static pressure has been applied due to high airtightness and high-rise housing and the installation of filters to improve air quality. A multi-blade fan with relatively small size and high static pressure and high air volume is used.

  Hereinafter, this type of multi-blade impeller and multi-blade fan will be described with reference to FIGS. 8 and 9.

  As shown in the figure, the multiblade blower 101 is sandwiched between a suction plate 103 having a bell mouth-like suction port 102 and a back plate 104 opposite to the suction plate 103 and sandwiching a side wall 106 having a discharge port 105. A multi-blade impeller 111 having a casing 107 configured, a blade 109 annularly arranged on a disk-shaped main plate 108, and a side plate 110 attached to the tip of the blade for reinforcement is provided on the back plate 104. It is the structure connected with the rotating shaft 113 of the attached electric motor 112 (for example, refer patent document 1).

This conventional multi-blade fan is provided with 40 to 50 blades 109, and the shape thereof is an outlet angle 114 of 125 to 137 °, an inlet angle 115 of 58 to 63 °, and a ratio of inner diameter to outer diameter (hereinafter referred to as inner and outer diameters). (Referred to as a diameter ratio) is 0.82 to 0.86, which is almost the same as that of a general multiblade fan.
Japanese Patent No. 3490678

  As a characteristic of the multiblade fan, when a high external static pressure is applied, the suction flow 117 moves toward the suction port 102 and only works on a part of the blade 109. In the multiblade blower 101, the chord length of the blade 109 is small, the inlet angle 115 and the outlet angle 114 do not match the flow direction, and the number of blades 109 is 40 to 50. In general, it is known that the blade inner diameter D ′ of the multi-blade impeller 111 may be reduced in order to reduce noise when high static pressure is applied. However, if the blade inner diameter D ′ is reduced, there is a problem that the air volume when low static pressure is applied decreases, and turbulent noise when high static pressure is applied without reducing the air volume when low static pressure is applied. The low It is required to.

  An object of the present invention is to solve such a conventional problem and to reduce noise and turbulent noise when high static pressure is applied without reducing the air volume when low static pressure is applied.

In order to achieve the above object, a blower of the present invention is a multi-blade impeller comprising a disk-shaped main plate and a plurality of blades arranged annularly on the main plate, and rotating around the center of the main plate. The ratio of the inner diameter D1 to the outer diameter D2 on the side is 0.7 to 0.8, the ratio of the inner diameter D1 to the outer diameter D2 on the tip side of the blade is 0.8 to 0.9, and the number of blades Z is Z = (π × D2) / (t × a)
Where t: blade average thickness, a: constant, 4.5 <a <6.0
A multi-blade impeller characterized by satisfying

  By this means, the blade area is large and the interval between the blades can be set appropriately, so the flow between the blades can be made smooth, and the flow separation when high static pressure is applied is suppressed to reduce noise. In addition, a multiblade impeller having a wide suction port and capable of suppressing a decrease in air volume even when a low static pressure is applied can be obtained.

  Another means is a multiblade impeller characterized in that the winding angle θ is 3.5 ° to 7 °.

  By this means, it is possible to accurately change the flow direction by the blade, and it is possible to obtain a multiblade impeller capable of reducing noise by suppressing separation of the flow when high static pressure is applied.

  Another means is a multiblade impeller characterized in that the inlet angle at the tip of the blade is 66 ° to 78 ° and the outlet angle is 160 ° to 172 °.

  By this means, the blade inlet angle and outlet angle can be set to appropriate angles that can suppress the collision and separation of the flow, and the noise during high static pressure application can be reduced without reducing the air volume during low static pressure application. A multiblade impeller that can be reduced is obtained.

  Another means is a multiblade impeller characterized in that the inner diameter of the blade increases toward the blade tip in a range of 50% to 70% from the blade tip in the total axial length of the blade. .

  By this means, when high static pressure is applied, the main flow tends to be biased toward the tip of the blade, but the main flow can be guided to the main plate side of the blade to increase the working area of the blade, and back flow on the main plate side of the blade is suppressed. Thus, a multiblade impeller that can reduce noise when a high static pressure is applied is obtained.

  Another means is a multiblade impeller characterized in that a plurality of substantially fan-shaped holes including an arc having the same diameter as the inner diameter of the blade are arranged in an annular shape in the main plate.

  This means that when the main plate has a cone shape, it is difficult to prevent air from flowing into the joint between the blade and the main plate, and the noise when high static pressure is applied is reduced without reducing the air volume when low static pressure is applied. A multiblade impeller that can be reduced is obtained.

  Another means is a multi-blade impeller characterized in that the number of holes in the main plate is six.

  By this means, when the multi-blade impeller is manufactured by resin molding, a multi-blade impeller capable of achieving both the strength of the multi-blade impeller itself and the improvement of the fluidity of the resin during molding can be obtained.

  Another means is a multiblade impeller characterized in that the main plate outer diameter is smaller than the blade outer diameter.

  By this means, it is possible to suppress the flow between the blades from colliding with the main plate at the time of applying a low static pressure, and it is possible to obtain a multiblade impeller capable of suppressing a decrease in the air volume.

  Another means is a multi-blade fan comprising the multi-blade impeller according to any one of claims 1 to 7 inside a scroll casing having a bell mouth-like suction orifice and a spiral side wall. Is.

  By this means, the dynamic pressure of the air flowing out from the multi-blade impeller can be efficiently led to the discharge port while being converted to static pressure, and the air flow at the time of applying high static pressure can be reduced without reducing the air volume at the time of applying low static pressure. A multiblade fan capable of reducing noise is obtained.

  Another means is a multiblade blower characterized in that the expansion angle of the scroll casing is 6.5 ° to 7.5 °.

  By this means, the degree of increase in the flow area of the air flowing out from the multi-blade impeller can be set appropriately, and the noise when high static pressure is applied is reduced without reducing the air volume when low static pressure is applied. A multi-blade fan is obtained.

  Another means is a multiblade fan characterized in that the gap between the tongue of the scroll casing and the blade is 6% to 9% of the outer diameter D2 of the blade.

  By this means, the interference noise between the tongue and the blade can be reduced without reducing the blowing efficiency of the multiblade blower, and the noise when applying high static pressure is reduced without reducing the air volume when applying low static pressure. A multiblade blower that can be obtained is obtained.

  Another means is a multiblade blower characterized in that the height of the tongue in the plan view of the scroll casing is 30% to 40% with respect to the blade outer diameter D2.

  By this means, by appropriately setting the length of the spiral from the tongue of the scroll casing to the discharge port and the flow path area, the noise at the time of applying high static pressure is reduced without reducing the air volume at the time of applying low static pressure. A multi-blade fan is obtained.

  Another means is a multiblade fan characterized in that the suction orifice and the blade overlap each other in the axial direction with a length of 1 to 5% of the axial length of the blade.

  By this means, it is possible to suppress the generation of noise and backflow due to the collision of airflow at the blade tip, and it is possible to suppress the generation of shear flow due to the interference between the blade and the suction orifice. A multiblade blower capable of reducing noise during application of high static pressure without lowering the pressure is obtained.

  ADVANTAGE OF THE INVENTION According to this invention, the multiblade impeller and multiblade fan which can reduce the noise at the time of high static pressure addition can be provided, without reducing the air volume at the time of low static pressure addition.

The invention according to claim 1 of the present invention is a multi-blade impeller comprising a disk-shaped main plate and a plurality of blades arranged annularly on the main plate, and rotating around the center of the main plate. The ratio of the inner diameter D1 to the outer diameter D2 of the blade is 0.7 to 0.8, the ratio of the inner diameter D1 to the outer diameter D2 on the blade tip side is 0.8 to 0.9, and the number of blades Z is Z = (π × D2) / (t × a)
Where t: blade average thickness, a: constant, 4.5 <a <6.0
It is a multi-blade impeller characterized by satisfying the requirements.The blade area is large, and the interval between the blades can be set appropriately, so that the flow between the blades can be made smooth. It is possible to reduce the noise and turbulent noise by suppressing the separation of the flow of air, and to reduce the air volume even when the suction port is wide and low static pressure is applied.

  In addition, the multi-blade impeller is characterized in that the winding angle θ is 3.5 ° to 7 °, and the flow direction can be accurately turned by the blade, and when high static pressure is applied. It has an effect that noise can be reduced by suppressing flow separation.

  The blade has a multiblade impeller characterized in that the inlet angle at the tip of the blade is 66 ° to 78 ° and the outlet angle is 160 ° to 172 °. It is possible to set the angle at an appropriate angle that can suppress the collision and separation, and it is possible to reduce noise at the time of applying high static pressure without reducing the air volume at the time of applying low static pressure.

  Further, the blade has a high static pressure in which the inner diameter of the blade increases toward the blade tip in a range of 50% to 70% from the blade tip in the total axial length of the blade. At the time of addition, the main flow tends to be biased toward the tip of the blade, but the main flow can be guided to the main plate side of the blade to increase the working area of the blade. It has the effect | action that a noise can be reduced.

  Further, a multi-blade impeller characterized in that a plurality of substantially fan-shaped holes including an arc having the same diameter as the inner diameter of the blade are arranged in an annular shape on the main plate, and the main plate has a cone shape. In this case, it is possible to suppress the air from becoming difficult to flow into the joint between the blade and the main plate, and to reduce the noise at the time of applying the high static pressure without reducing the air volume at the time of applying the low static pressure.

  In addition, the multi-blade impeller is characterized in that the number of holes in the main plate is six. When the multi-blade impeller is manufactured by resin molding, the strength and molding of the multi-blade impeller itself It has the effect of improving both the fluidity of the resin at the time.

  In addition, it is a multi-blade impeller characterized in that the main plate outer diameter is smaller than the blade outer diameter, and it is possible to suppress the flow between the blades from colliding with the main plate when low static pressure is applied, and the air volume is reduced. It has the effect | action that it can suppress.

  Moreover, it is a multi-blade fan characterized by comprising the multi-blade impeller according to any one of claims 1 to 7 inside a scroll casing having a bell mouth-shaped suction orifice and a spiral side wall, The dynamic pressure of the air flowing out from the multi-blade impeller can be guided to the discharge port while efficiently converting to static pressure, reducing the noise when applying high static pressure without reducing the air volume when applying low static pressure. It has the effect of being able to.

  In addition, the multi-blade blower is characterized in that the expansion angle of the scroll casing is 6.5 ° to 7.5 °, and the degree of increase in the flow path area of the air flowing out from the multi-blade impeller is appropriate. Therefore, the noise at the time of applying high static pressure can be reduced without reducing the air volume at the time of applying low static pressure.

  Moreover, it is set as the multiblade fan characterized by the clearance gap between the tongue part of a scroll casing and a braid | blade being 6 to 9% of the outer diameter D2 of a braid | blade, and reduces the ventilation efficiency of a multiblade fan Therefore, the interference noise between the tongue and the blade can be reduced, and the noise when the high static pressure is applied can be reduced without reducing the air volume when the low static pressure is applied.

  The tongue height in the plan view of the scroll casing is 30% to 40% with respect to the blade outer diameter D2. By appropriately setting the length of the vortex and the flow path area, there is an effect that noise at the time of applying high static pressure can be reduced without reducing the air volume at the time of applying low static pressure.

  Further, the suction orifice and the blade have a length of 1 to 5% of the axial length of the blade and overlap with each other in the axial direction. Noise generation and back flow can be suppressed, and generation of shear flow due to interference between the blade and the suction orifice can be suppressed, and noise when high static pressure is applied without reducing the air volume when low static pressure is applied. It has the effect that can be reduced.

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

(Embodiment 1)
A first embodiment of the present invention will be described with reference to FIGS. As shown in FIGS. 1 to 4, a multi-blade fan 1 used as a ceiling-embedded ventilation fan attached to a ceiling to ventilate a space such as a bathroom or a toilet is composed of an upper surface 2, a lower surface 3, and a part of a side surface 4. Is an outer shell 5 that is 230 mm square and 175 mm in height, a flat top plate 6 that is fixed to the upper surface 2 of the outer shell 5, an electric motor 7 that is fixed to the top plate 6, and a multiplicity that is fixed to the electric motor 7. A blade impeller 8, a scroll casing 9 fixed so as to cover the multi-blade impeller 8, and an adapter 11 communicating with the discharge port 10 of the scroll casing 9 and the opening of the side surface 4 of the outer shell 5 are provided.

  The multi-blade impeller 8 includes a main plate 12 having a main plate outer diameter Dm of 130 mm and a thickness of 3 mm, 59 blades 13 having a blade height Hb of 96 mm arranged annularly on the outer peripheral side of the main plate 12, and a blade tip portion 14 is provided with an annular plate 15 having an outer diameter of 148.5 mm and a height of 3 mm attached to the outer periphery of 14 and six substantially fan-shaped holes 16 arranged annularly on the main plate 12.

  The blade 13 has a blade outer diameter D2 of 143.5 mm and larger than the main plate outer diameter Dm (130 mm), and the main plate side blade inner diameter D1b is an inner / outer diameter ratio (D1b / D2) of the ratio of the main plate side blade inner diameter D1b to the blade outer diameter D2. Of the blade 13 is 122 mm, where the inner-outer diameter ratio (D1t / D2) of the ratio of the tip-side blade inner diameter D1t to the outer diameter D2 is 0.85. The blade inner diameter gradually increases from the blade tip 14 toward the blade tip 14 from a position of 40 mm in the direction of the rotation axis 17. The blade 13 has a tip side thickness of 0.8 mm, a root side thickness of 2.5 mm, and a blade average thickness t of 1.65 mm.

  Here, the inlet angle α, the outlet angle β, and the winding angle θ of the blade 13 are defined as follows. As shown in FIG. 5, the entrance angle α is the blade center line 19 of the blade 13 at the intersection of the blade inner circumferential circle 18 and the blade center line 19 of the blade 13 on the cross section perpendicular to the rotation axis 17. The angle between the extended straight line and the rotation direction 20 side of the blade inner circumference 18. Similarly, the exit angle β is an extension straight line and an outer periphery of the blade center line 19 of the blade 13 at the intersection of the blade outer periphery circle 21 and the blade center line 19 of the blade 13 on the cross section perpendicular to the rotation shaft 17. This is the angle between the rotation direction 20 of the circle 21 and the opposite side. The winding angle θ is a line connecting the intersection L1 between the intersection of the blade inner circle 18 and the blade center line 19 of the blade 13 and the rotary shaft 17 and the intersection of the blade outer circle 21 and the blade center line 19 of the blade 13. The angle formed by the minute L2.

  In the present embodiment, the entrance angle on the root side is 67 degrees, the exit angle is 18 degrees, and the winding angle is 5.5 degrees.

  The main plate 12 of the multi-blade impeller 8 has a main plate center portion 22 protruding 44 mm toward the blade tip portion 14 side, and is gently inclined from the main plate center portion 22 toward the outer periphery to have a cone shape.

  The hole 16 of the main plate 12 is substantially fan-shaped when viewed from the direction of the rotary shaft 17, and for example, the outer diameter Dh of the substantially fan-shaped hole is 112 mm, which is the same as the main plate-side blade inner diameter D1b.

  The scroll casing 9 includes a suction plate 24 having a bell mouth-shaped suction orifice 23 concentric with the multi-blade impeller 8 and having a suction orifice inner diameter Do of 113 mm, and a spiral side wall 25 having a scroll casing side wall height Hc of 117 mm. The gap Cl between the blade casing 13 and the portion where the scroll casing 9 and the blade 13 are closest (hereinafter referred to as the tongue portion 26) is 9.7 mm.

  Here, the expansion angle αc and the tongue height Th of the scroll casing 9 are defined as follows.

  6 (a) and 6 (b), on the cross section of the surface perpendicular to the rotation shaft 17, the enlarged angle αc is the creepage from the tongue portion 26 of the side wall 25 of the scroll casing 9 on the horizontal axis. The distance is the angle of inclination of the graph in which the vertical axis represents the distance from the rotary shaft 17 to the side wall 25 of the sucrose casing 9. The tongue height Th is a distance between a straight line Lo parallel to the straight line portion 27 at the end of winding of the side wall 25 of the scroll casing 9 and passing through the rotation center, and a tangent line L3 parallel to the straight line Lo and in contact with the tongue portion.

  In the present embodiment, the enlargement angle αc is 6.9 degrees, and the tongue height Th is 51 mm.

  Moreover, the end face 28 of the bell mouth-shaped suction orifice 23 is inserted into the multi-blade impeller 8, and the suction orifice 23 and the blade 13 overlap each other in the direction of the rotary shaft 17 by 2 mm.

  With this configuration, when the multiblade impeller 8 is rotated by applying a driving force from the electric motor 7, the suction air 29 is smoothly guided to the multiblade impeller 8 by the bell mouth-shaped suction orifice 23 and flows into the blade 13. Then, the pressure is increased, and the dynamic pressure is gradually converted into a static pressure when flowing out of the blade 13 and passing through the spiral scroll casing 9 and discharged from the discharge port 10 to the outside through the adapter 11.

  At this time, the inner / outer diameter ratio of the ratio of the inner diameter to the outer diameter on the main plate 12 side of the blade 13 is in the range of 0.7 to 0.8, and the inner / outer diameter is the ratio of the inner diameter to the outer diameter at the blade tip portion 14. Since the ratio is in the range of 0.8 to 0.9, the suction orifice inner diameter Do can be increased while the area of the blade 13 is increased, so that a reduction in air volume can be suppressed even when a low static pressure is applied. it can. In addition, the number of blades 13 satisfies the formula (1) and the interval between the blades 13 is set appropriately, so that the flow between the blades 13 can be made smooth and the separation of the flow when applying static pressure is suppressed. Noise can be reduced. Formula (1) is shown below.

Z = (π × D2) / (t × a) --- Formula (1)
Where t: blade average thickness, a: constant, 4.5 <a <6.0

  Further, since the winding angle θ is in the range of 3.5 ° to 7 °, the direction of flow can be accurately turned by the blade 13, and the separation of the flow when high static pressure is applied is suppressed to reduce noise. can do.

  In addition, the inlet angle α at the blade tip 14 is in the range of 66 ° to 78 ° and the outlet angle β is in the range of 160 ° to 172 °. Noise at the time of applying high static pressure can be reduced without reducing the air volume at the time of applying static pressure.

  Further, when high static pressure is applied, the main flow 30 tends to be biased toward the blade tip 14, but the blade 30 moves toward the blade tip 14 within a range of 50% to 70% of the total length in the direction of the rotation axis 17 of the blade 13. Since the inner diameter of the blade 13 is increased, it is possible to increase the region where the blade 13 works by guiding the main flow to the main plate 12 side of the blade 13, and suppresses the back flow of the blade 13 on the main plate 12 side, thereby increasing the high static pressure. Noise during addition can be reduced.

  Although the main plate 12 has a cone shape, the outer diameter Dh of the substantially fan-shaped hole annularly arranged in the main plate 12 is the same diameter as the main plate-side blade inner diameter D1b. It is possible to prevent the air from flowing into the air, and to reduce the noise when the high static pressure is applied without lowering the air volume when the low static pressure is applied, and a part of the flow flowing out from the blade 13 is the main plate. When the back side surface 31 of the main body 12 flows backward and flows into the blade 13 again through the hole 16 of the main plate 12, a disturbance is generated by the outer peripheral edge of the hole 16, and the inflow into the blade 13 is disturbed, and the blowing efficiency is lowered. Generation of flow noise can be suppressed. The substantially fan-shaped hole 16 has a function of guiding the intake air 29 to the electric motor 7 and promoting the cooling of the electric motor 7. Further, since the number of the holes 16 in the main plate 12 is 6, when the multi-blade impeller 8 is manufactured by resin molding, both the strength of the multi-blade impeller 8 itself and the improvement of the fluidity of the resin during molding are achieved. be able to.

  Further, since the outer diameter Dm of the main plate 12 is smaller than the blade outer diameter D2, it is possible to suppress the flow between the blades 13 from hitting the main plate 12 when a low static pressure is applied, and it is possible to suppress a decrease in the air volume.

  Further, the expansion angle αc of the scroll casing 9 is in the range of 6.5 ° to 7.5 °, and the degree of increase in the flow area of the air flowing out from the multi-blade impeller 8 is appropriately set. Noise at the time of applying high static pressure can be reduced without reducing the air volume at the time of applying static pressure.

  Further, since the clearance Cl between the tongue 26 of the scroll casing 9 and the blade 13 is 6% to 9% of the blade outer diameter D2, the interference between the tongue 26 and the blade 13 without reducing the blowing efficiency of the multiblade fan 1. Noise can be reduced, and noise when high static pressure is applied can be reduced without reducing the air volume when low static pressure is applied.

  Further, the height Th of the tongue in the plan view of the scroll casing 9 is in the range of 30% to 40% with respect to the blade outer diameter D2, and the length of the spiral from the tongue 26 of the scroll casing 9 to the discharge port 10 and the flow path. The area is set appropriately, and noise at the time of applying high static pressure can be reduced without reducing the air volume at the time of applying low static pressure.

  Further, the suction orifice 23 and the blade 13 are 1 to 5% of the length of the blade 13 in the direction of the rotary shaft 17 and overlap in the direction of the rotary shaft 17. In addition, the generation of shear flow due to the interference between the blade 13 and the suction orifice 23 can be suppressed, and the noise when high static pressure is applied is reduced without reducing the air volume when low static pressure is applied. be able to.

  The multi-blade impeller 8 and the scroll casing 9 can obtain the same effect even if they have a grade of a draft grade applied in the case of resin molding or have irregularities such as ribs for strength reinforcement.

  Although the top plate 6 has a flat plate shape, the same effect can be obtained even if there is an embossing, a hole, or a bend of the outer periphery for strength reinforcement or attachment of other components.

  Although the top plate 6 is fixed to the outer shell 5, the same effect can be obtained even when the unit formed by joining the top plate 6 and the scroll casing 9 is fixed to the outer shell 5.

  FIG. 7 shows a comparison between the air volume-static pressure characteristics and the noise characteristics of the conventional multi-blade fan as the effect of the multi-blade impeller 8 and the multi-blade fan 1 according to the first embodiment of the present invention.

  The multi-blade fan of the conventional shape is the same as the multi-blade fan 1 of the first embodiment of the present invention in the maximum outer dimensions of the scroll casing 9 and the outer dimensions of the multi-blade impeller 8. The design factors shown in the invention are different.

  From FIG. 7, it can be seen that the multiblade fan 1 according to Embodiment 1 of the present invention can improve aerodynamic performance and reduce noise when high static pressure is applied without reducing the air volume when low static pressure is applied.

  The present invention provides a multi-blade impeller and a multi-blade fan that can reduce noise when a high static pressure is applied without lowering the air volume when a low static pressure is applied. It can be used for equipment.

The perspective view which shows the multiblade air blower of Embodiment 1 of this invention. 1 is a side sectional view showing a multiblade impeller and a multiblade fan according to Embodiment 1 of the present invention. The lower surface fragmentary sectional view which shows the multiblade impeller and multiblade fan of Embodiment 1 of this invention The perspective view which shows the multiblade impeller of Embodiment 1 of this invention Root side sectional view of the blade of the multiblade impeller of Embodiment 1 of the present invention The figure which shows the shape of the scroll casing of the multiblade fan of Embodiment 1 of this invention ((a) same external view, (b) figure which shows the graph showing the same enlarged angle) Performance comparison diagram between the multiblade fan of Embodiment 1 of the present invention and the multiblade fan of the prior art Side sectional view showing a conventional multi-blade impeller and multi-blade fan Sectional view showing a conventional multi-blade impeller

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Multiblade blower 2 Upper surface 3 Lower surface 4 Side surface 5 Outer shell 6 Top plate 7 Electric motor 8 Multiblade impeller 9 Scroll casing 10 Discharge port 11 Adapter Dm Main plate outer diameter 12 Main plate Hb Blade height 13 Blade 14 Blade tip 15 Annular plate 16 Hole D2 Blade outer diameter D1b Main plate side blade inner diameter D1t Tip side blade inner diameter 17 Rotating shaft t Blade average thickness α Inlet angle β Outlet angle θ Wound angle 18 Blade inner circle 19 Blade center line 20 Rotating direction 21 Blade outer circle L1 Line segment L2 line segment 22 main plate center portion Dh hole outer diameter Do suction orifice inner diameter 23 suction orifice 24 suction plate Hc scroll casing side wall height 25 side wall 26 tongue portion Cl clearance αc enlarged angle Th tongue portion height 27 straight portion Lo straight portion L3 tangent line 28 End face 29 Suction air 30 Main flow 3 1 Back side

Claims (12)

A multi-blade impeller comprising a disk-shaped main plate and a plurality of blades arranged in an annular shape on the main plate and rotating about the center of the main plate, and an inner diameter D1 and an outer diameter D2 of the blade on the main plate side The ratio of the inner diameter D1 and the outer diameter D2 on the tip side of the blade is 0.8 to 0.9, and the number of blades Z is Z = (π × D2) / (t × a)
Where t: blade average thickness, a: constant, 4.5 <a <6.0
A multi-blade impeller characterized by satisfying The multiblade impeller according to claim 1, wherein the winding angle θ is 3.5 ° to 7 °. The multiblade impeller according to claim 1 or 2, wherein an inlet angle at a tip of the blade is 66 ° to 78 °, and an outlet angle is 160 ° to 172 °. The multiblade impeller according to any one of claims 1 to 3, wherein an inner diameter of the blade increases toward the blade tip in a range of 50% to 70% from the blade tip in a total axial length of the blade. . The multiblade impeller according to any one of claims 1 to 4, wherein a plurality of substantially fan-shaped holes including an arc having the same diameter as the inner diameter of the blade in an outer shape are annularly arranged in the main plate. The multiblade impeller according to claim 5, wherein the number of holes in the main plate is six. The multiblade impeller according to any one of claims 1 to 6, wherein an outer diameter of the main plate is smaller than an outer diameter of the blade. A multi-blade blower comprising the multi-blade impeller according to any one of claims 1 to 7 in a scroll casing having a bell mouth-like suction orifice and a spiral side wall. The multiblade blower according to claim 8, wherein an expansion angle of the scroll casing is 6.5 ° to 7.5 °. The multiblade fan according to claim 8 or 9, wherein a gap between the tongue of the scroll casing and the blade is 6% to 9% of the outer diameter D2 of the blade. The multi-blade fan according to any one of claims 8 to 10, wherein a height of a tongue portion in a plan view of the scroll casing is 30% to 40% with respect to a blade outer diameter D2. The multiblade fan according to any one of claims 8 to 11, wherein the suction orifice and the blade overlap each other in the axial direction with a length of 1 to 5% of the axial length of the blade.

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