JP2017082802A - Centrifugal fan - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a centrifugal fan showing superior hydrostatic pressure characteristic and air amount characteristic as well as low noise.SOLUTION: A central fan of this invention comprises an impeller 10, an impeller case 20, a motor 30 and a motor case 21. The impeller 10 has a boss part 11 connected to a shaft 31 coaxially rotated with a rotating shaft, a hub 12 extending from the boss part 11 toward outside in a radial direction and a plurality of vanes 13. The plurality of vanes 13 extend toward outside in a radial direction and an inner wall of the impeller case 20 has an inner surface expanding along the upper ends of the plurality of vanes 13 toward outside in a radial direction, a side end part 20a of a suction port 40 placed at a central part of the impeller case 20 has a curved surface protruding inside in a radial direction, the plurality of vanes have an axial upper end protruding upward at the outside in a radial direction rather than the inner-most end in a radial direction at the curved surface of the suction port and a distance between the several vanes and the inside surface of the impeller case becomes the shortest distance at the upper side ends in an axial direction of the several vanes.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a centrifugal fan.

  In the centrifugal fan, the gas sucked from the intake port is pushed outward in the radial direction by the centrifugal force generated by the rotation of the impeller, and further passes through the annular wind tunnel provided around the impeller and turns in the circumferential direction. The gas is discharged from the exhaust port to the outside.

  In general, in medical devices such as artificial respirators and evacuation devices, it is necessary to flow a gas using a centrifugal fan for the purpose of assisting breathing or suction. Centrifugal fans used in such devices are required to have low noise from the use environment of medical devices in addition to high static pressure and air volume.

  For example, Japanese Patent Application Laid-Open No. 9-14192 discloses a centrifugal fan in which an airflow guide is provided at a suction port to reduce noise.

Japanese Patent Laid-Open No. 9-14192

  In JP-A-9-14192, the ratio of the area of a virtual ring connecting the tips on the center side of the blades of the centrifugal impeller and the inlet area of the suction port is optimized, and the airflow at the suction port is An airflow guide that guides smoothly is provided. In addition, the airflow guide is formed so that the cross-sectional shape thereof is an arc shape, and a seal member that is in sliding contact with an inlet portion formed in the center of the side plate of the centrifugal impeller is attached to the inside of the arc to seal the airtightness of the suction port. Keep trying. That is, in order to have high static pressure and low noise, it is necessary to provide an airflow guide and a seal member, and the structure becomes complicated.

  The present invention has been made in view of such points, and its main object is to provide a centrifugal fan having a simple structure suitable for downsizing, excellent static pressure characteristics and air flow characteristics, and low noise. is there.

An exemplary centrifugal fan of the present invention includes an impeller that rotates about a rotation shaft, an impeller case that houses the impeller, a motor that rotationally drives the impeller, and a motor case that is coupled to the impeller case and houses the motor. The impeller includes a boss portion coupled to a shaft that rotates about a rotation axis, a hub extending radially outward from the outer peripheral surface of the boss portion, and a plurality of blades provided on the upper surface of the hub, The plurality of blades extend radially outward from the rotation shaft, and the inner wall of the impeller case that covers the plurality of blades has an inner surface that extends radially outward along the upper ends of the plurality of blades. The impeller case has an air inlet at the center, the air inlet has a curved surface protruding radially inward, and the plurality of blades are arranged from the radially innermost end of the curved surface of the air inlet. Also on the outside in the radial direction Has an axial upper end which projects in the axial direction upper end of the plurality of blades, the distance between the inner surfaces of the plurality of blades and the impeller casing is shortest.

  ADVANTAGE OF THE INVENTION According to this invention, the centrifugal fan which is excellent in a static pressure characteristic and an air volume characteristic, and can also provide low noise can be provided.

It is sectional drawing which showed the structure of the centrifugal fan in one Embodiment of this invention. It is the top view which showed the structure of the impeller in one Embodiment of this invention. It is sectional drawing of the centrifugal fan which showed the other structure of the impeller. It is the enlarged view which showed the vicinity of the side edge part of the inlet port of FIG. It is sectional drawing which showed the structure of the centrifugal fan in other embodiment of this invention.

  Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings. In the description of the present embodiment, a direction parallel to the rotation axis is referred to as an “axial direction”, a radial direction around the rotation axis is referred to as a “radial direction”, and a circumferential direction around the rotation axis is referred to as a “circumferential direction”. It is said. Also, the shape and positional relationship of each part will be described with the direction along the axial direction as the vertical direction and the impeller side as the top with respect to the motor.

  The present invention is not limited to the following embodiment. Changes can be made as appropriate without departing from the scope of the effects of the present invention. Furthermore, combinations with other embodiments are possible.

  FIG. 1 is a cross-sectional view schematically showing the configuration of a centrifugal fan 100 in one embodiment of the present invention. FIG. 2 is a plan view showing the configuration of the impeller 10 according to the embodiment of the present invention. FIG. 3 is a cross-sectional view of a centrifugal fan showing another configuration of the impeller 10.

  As shown in FIG. 1, the centrifugal fan 100 according to the present embodiment includes an impeller 10 that rotates about a rotation axis J, an annular wind tunnel portion 50 that is provided around the impeller 10, and an intake port that is above the impeller 10. An impeller case 20 that accommodates the impeller 10 while being provided 40, a motor 30 that rotationally drives the impeller 10, and a motor case 21 that is connected to the impeller case 20 and accommodates the motor 30 are provided.

  The impeller 10 includes a boss portion 11 coupled to a shaft 31 that rotates coaxially with the rotation axis J, a hub 12 that extends radially outward from the outer peripheral surface of the boss portion 11, and a plurality of provided on the upper surface of the hub 12. And blades 13.

  The boss portion 11 is coupled to the outer peripheral surface of the shaft 31 extending vertically along the rotation axis J in a substantially cylindrical shape above the motor 30. As a result, the holding strength of the shaft 31 is improved, and the deflection of the shaft 31 due to the rotation of the impeller 10 can be suppressed.

  Further, the boss portion 11 may be provided with a lid portion that protrudes upward while covering the upper end portion of the shaft 31. The lid part has a curved surface. Thereby, the gas sucked from the side end portion 20a of the intake port 40 efficiently flows into the wind tunnel portion 50 along the curved surface, and the static pressure and air flow characteristics are improved.

  The upper surface of the hub 12 is an inclined surface 12a inclined radially outward from the outer peripheral surface of the boss portion 11 and a flat surface extending substantially perpendicularly to the rotation axis J from the radially outer end of the inclined surface 12a. 12b. Thereby, the gas sucked from the intake port 40 efficiently flows into the wind tunnel portion 50 along the inclined surface 12a, and the static pressure and the air volume characteristics are improved. The inclined surface 12a may not be an inclined surface with a constant inclination, but may be a curved surface with a non-constant inclination.

  The inclined surface 12a preferably has a curved surface that is recessed radially inward and downward. Thereby, a space is provided on the radially outer side of the boss portion 11, and the gas sucked from the intake port 40 efficiently flows into the wind tunnel portion 50 along the curved surface. Furthermore, in other words, a wide intake flow path of the intake port 40 can be secured, and the static pressure and air flow characteristics are improved.

  It is preferable that the peripheral edge of the flat surface 12 b of the hub 12 protrudes radially outward from the peripheral edges of the plurality of blades 13. By the rotation of the plurality of blades 13, the gas sucked from the air inlet 40 is discharged radially outward and flows into the wind tunnel portion 50. At this time, if the peripheral edge of the flat surface 12b protrudes radially outward from the peripheral edges of the plurality of blades 13, the gas flowing from the air inlet 40 to the wind tunnel portion 50 is unlikely to flow backward to the air inlet 40 side. As a result, since the gas density of the wind tunnel portion 50 is increased, the static pressure can be increased.

  Moreover, it is preferable that the hub 12 has an inclined surface that is inclined radially outward toward the lower side on the radially outer side of the periphery of the flat surface 12b. Thereby, the gas sucked from the intake port 40 can be efficiently poured into the wind tunnel portion 50. The inclined surface is not an inclined surface with a constant inclination, and may be a curved surface with a non-constant inclination.

  As shown in FIG. 1, the plurality of blades 13 extend radially outward from the rotation axis J in a cross-sectional view. Further, the plurality of blades 13 have a radially inner end 13a positioned on the innermost radial direction, an axial upper end 13b protruding upward, and a radially outer end 13c positioned on the outermost radial direction. Yes. That is, the plurality of blades 13 extend radially outward and upward from the radially inner end 13a toward the axial upper end 13b, and radially outward and upward from the axial upper end 13b to the radially outer end 13c. It extends downward. However, as shown in FIG. 3, the plurality of blades 13 may extend radially outward and downward from the radially inner end 13a.

  Further, as shown in FIG. 2, the plurality of blades 13 are radially extended outward in the radial direction while being inclined in the same direction as the rotation direction of the centrifugal fan 100 in a plan view. Further, the plurality of blades 13 includes a main wing 15 and an auxiliary wing 16, and two auxiliary wings 16 are provided between the main wings 15 in the circumferential direction. However, only one auxiliary wing 16 may be provided between the main wings 15. That is, the main wings 15 and the auxiliary wings 16 may be alternately arranged in the circumferential direction.

  The inner wall of the impeller case 20 that covers the plurality of blades 13 has an inner side surface 20b that extends radially outward along the upper ends of the plurality of blades 13. The upper ends of the plurality of blades 13 and the inner side surface 20b of the impeller case 20 face each other substantially in parallel. Preferably, the main wing 15 and the auxiliary wing 16 are opposed to the inner side surface 20b of the impeller case 20 substantially in parallel to the outer side in the radial direction with respect to each axial upper end 13b.

  The impeller case 20 has an air inlet 40 at the center, and has a curved surface protruding inward in the radial direction at the side end 20a of the air inlet 40. Here, the gas sucked from the intake port 40 is exhausted from the exhaust port (not shown) after passing through the wind tunnel 50 and turning in the circumferential direction by the rotation of the impeller 10.

  The motor 30 includes a bearing 32 that rotatably supports the rotor magnet 33 around the rotation axis J, a bearing holding portion 35 that supports the bearing 32, and a stator 34 that is supported by the bearing holding portion 35. . The hub 12 fixed to the shaft 31 that rotates about the rotation axis J includes a substantially cylindrical rotor holding portion 12c that extends downward, and the rotor magnet 33 is fixed to the inner peripheral surface of the rotor holding portion 12c. Yes. The motor 30 illustrated in FIG. 1 is an outer rotor type motor, but may be an inner rotor type motor.

  By supplying drive current to the stator 34, rotational torque is generated between the rotor magnet 33 and the stator 34. Thereby, the impeller 10 fixed to the shaft 31 rotates around the rotation axis J.

  The motor case 21 has a motor housing portion 21a that surrounds the motor 30 from the radially outer side, and a concave portion 21b that is recessed downward on the radially outer side of the motor housing portion 21a. The motor housing portion 21a is disposed on the radially outer side of the rotor holding portion 12c. The recess 21b is connected to the impeller case 20 at the radially outer end.

  The recess 21b has a curved surface. Since the recess 21b has a curved surface, the gas that has flowed into the recess 21b along the inner surface of the impeller case 20 from the intake port 40 efficiently flows from the radially outer side to the radially inner side of the recess 21b. The gas flowing inward in the radial direction of the recess 21b is added with a swirl component in the circumferential direction generated by the rotation of the impeller 10, and is pushed out toward the exhaust port (not shown). That is, since the concave portion 21b has a curved surface, the gas sucked from the intake port 40 is efficiently discharged from the exhaust port (not shown).

  In the present embodiment, the plurality of blades 13 are provided so that the radially inner ends 13a are located as radially as possible inside. In other words, the radially inner end 13 a is located more radially inward than the side end 20 a of the intake port 40. Thereby, since the gas sucked from the intake port 40 can be efficiently flowed into the wind tunnel portion 50 by the rotation of the plurality of blades 13, the static pressure can be increased. On the other hand, when the radially inner ends 13a of the plurality of blades 13 are positioned radially inward, the intake flow path of the intake port 40 becomes narrow and noise increases. In order to reduce the noise, it is necessary to make the opening of the intake port 40 small. However, if the opening of the intake port 40 is reduced, the air volume is reduced. Therefore, in the present embodiment, a curved surface that protrudes radially inward is provided at the side end 20a of the air inlet 40 in order to suppress a decrease in the air volume. Thereby, gas can be efficiently inhaled from the intake port 40, and a reduction in air volume can be suppressed. In addition, noise can be reduced.

  That is, in the present embodiment, in the centrifugal fan in which the radially inner ends 13a of the plurality of blades 13 are provided as radially as possible inside, the opening of the intake port 40 is reduced, and the side end portion 20a of the intake port 40 is By providing a curved surface protruding radially inward, static pressure and air volume can be increased and noise can be reduced.

  Further, in the present embodiment, the plurality of blades 13 extend radially outward from the rotation axis J, and the inner wall of the impeller case 20 extends radially outward along the upper end portions of the plurality of blades 13. It has an inner surface 20b. As a result, the gas sucked from the air inlet 40 by the rotation of the plurality of blades 13 is discharged radially outward toward the lower side, and thus efficiently flows into the wind tunnel portion 50.

  In the impeller 10 of the present embodiment, the boss portion 11, the hub 12, and the plurality of blades 13 may be integrally formed. For example, it may be molded as a continuous integral member by injection molding.

  Here, the amount of gas (air volume) sucked from the intake port 40 depends on the size of the opening of the intake port 40. Therefore, air flow characteristics can be improved by securing a wide intake flow path. Note that the size of the opening of the intake port 40 does not simply indicate the radial length of the side end portion 20a of the intake port 40 of the impeller case 20, but indicates the opening area of the side end portion 20a of the intake port 40.

  Note that the amount of gas (air volume) sucked from the intake port 40 is not only the size of the opening of the intake port 40 but also the shape of the side end portion 20a of the intake port 40 and the configuration around the intake port 40 and the intake port 40. It also depends on the positional relationship.

  Hereinafter, the shape of the side end portion 20a of the intake port 40 and the positional relationship between the intake port 40 and the configuration around the intake port 40 will be described with reference to FIG. However, in the present embodiment, the shape of the curved surface provided at the side end 20a of the intake port 40 is not particularly limited. FIG. 4 is an enlarged view showing the vicinity of the side end 20a of the intake port 40 of the impeller case 20 indicated by A in FIG.

  As shown in FIG. 4, the curved surface of the side end 20 a of the intake port has a radially innermost end P and an axially uppermost end Q. The curved surface of the side end 20a of the air inlet 40 protrudes radially outward with respect to a virtual line X connecting the radially innermost end P and the axially uppermost end Q. That is, the curved surface of the side end portion 20a of the intake port protrudes above the radially innermost end P of the curved surface of the side end portion 20a of the intake port 40. Thereby, gas can be suck | inhaled more efficiently along the curved surface of the side edge part 20a. As a result, the static pressure of the centrifugal fan 100 can be further increased.

  Further, the radially innermost end P has a minute R portion. Thereby, gas can be suck | inhaled more efficiently along R part. As a result, the static pressure of the centrifugal fan 100 can be further increased.

  The gas sucked from the intake port 40 has a high possibility of separation at the radially innermost end P. When the gas is separated, a turbulent flow occurs and it becomes difficult to efficiently suck the gas. For this reason, since the radially innermost end P has a minute R portion, it is possible to efficiently inhale the gas while suppressing gas separation at the radially innermost end P.

  In addition, since the curved surface of the side end portion 20a protrudes radially inward and upward as shown in FIG. 1, it can be easily formed.

Further, as shown in FIG. 4, the curved surface of the side end portion 20a of the inlet, the axial length L ₁ is preferably smaller than the radial length L _2. Thereby, since the air volume of the gas sucked from the intake port 40 increases, the air volume characteristics can be further improved.

Note that the length L ₁ in the axial direction, a line perpendicular to the rotational axis J passing through the axial uppermost Q, and a line parallel to the rotational axis J passing through the radial innermost end P, a point of intersection of, This is the shortest distance from the radially innermost end P. The length L ₂ of the radial refers the aforementioned intersection, that the shortest distance between the axial top end Q.

  In addition, it is preferable that the radially innermost end P having a minute R portion is located below the tangent line from the joint between the hub 12 and the auxiliary blade 16 to the side end portion 20a. That is, the joint between the hub 12 and the auxiliary wing 16 is located radially inward from the radially innermost end P. Thereby, gas can be suck | inhaled more efficiently, suppressing that gas peels in the radial direction innermost end P. FIG.

  In addition, the upper end portion of the boss portion 11 is positioned below the radially innermost end P of the side end portion 20a of the intake port 40. Further, the upper end portion of the boss portion 11 is located on the radially inner side with respect to the radially innermost end P of the side end portion 20 a of the intake port 40. As a result, a wide intake flow path of the intake port 40 can be secured, and the air flow characteristics are improved.

  Further, the main wing 15 extends from the radially innermost end P to the radially outer side from the radially innermost end P of the side end portion 20 a of the intake port 40. The axially upper end 13b of the main wing 15 is located radially outside the radially innermost end P of the side end 20a of the intake port 40. The auxiliary blade 16 extends from the radially innermost end P of the side end portion 20a of the intake port 40 from the radially outer side to the radially outer side.

  Further, the distance between the main wing 15 and the inner side surface 20b of the impeller case 20 is the shortest at the axially upper end 13b of the main wing 15. Thereby, the gas suck | inhaled by the inlet port 40 can be efficiently flowed into the wind tunnel part 50, and a static pressure can be raised. In addition, the distance between the auxiliary blade 16 and the inner surface 20b of the impeller case 20 is the shortest at the radially outer end 13c of the auxiliary blade 16. Thereby, it becomes easy to add a swirl component in the circumferential direction to the gas flowing into the wind tunnel portion 50, and the air volume can be increased.

  FIG. 5 is a cross-sectional view schematically showing the configuration of a centrifugal fan 110 according to another embodiment of the present invention. The centrifugal fan 110 in this embodiment is a so-called mixed flow fan.

  In the present embodiment, the configuration of the impeller 10 is different from the configuration illustrated in FIG. The configuration of the motor 30 is the same as that shown in FIG.

  The impeller 10 in the present embodiment is inclined radially outwardly from the boss portion 11 coupled to the shaft 31 rotating coaxially with the rotation axis J and a part of the outer peripheral surface of the boss portion 11 downward. It has a hub 12 and a plurality of blades 13 provided on the hub 12. Further, the inner walls of the plurality of blades 13 and the impeller case 20 are inclined along the inclination of the hub 12. That is, the plurality of blades 13, the inner wall of the impeller case 20, and the hub 12 are inclined substantially in parallel. Thereby, the gas sucked from the intake port 40 can be efficiently poured into the wind tunnel portion 50.

  The hub 12 is preferably inclined radially outward from the upper end of the outer peripheral surface of the boss 11 toward the lower side. Thereby, the shake of the shaft 31 due to the rotation of the impeller 10 can be further suppressed. In addition, the upper end part of the outer peripheral surface of the boss | hub part 11 means the site | part above the intermediate position between the uppermost end and the lowest end of the boss | hub part 11 among the outer peripheral surfaces of the boss | hub part 11.

  In the present embodiment as well, in the centrifugal fan in which the radially inner ends 13a of the plurality of blades 13 are provided on the radially inner side as much as possible, the opening of the intake port 40 is made small and the side end portion 20a of the intake port 40 is formed. By providing a curved surface protruding inward in the radial direction, the air volume can be increased and the noise can be reduced.

  Further, as shown in FIG. 5, an annular shroud 14 may be disposed at the upper end portions of the plurality of blades 13. Here, it is located on the radially outer side than the radially inner end 14 a of the shroud 14 and the radially outer end 12 d of the hub 12. Thereby, by rotation of the several blade | wing 13, while flowing in gas efficiently from the inlet port 40 to the wind tunnel part 50, it can suppress flowing back to the inlet port 40 side. As a result, a vortex is easily formed and stays in the wind tunnel 50, so that the static pressure can be increased.

DESCRIPTION OF SYMBOLS 10 Impeller 11 Boss part 12 Hub 12a Inclined surface 12b Flat surface 12c Rotor holding part 12d Radial outer end 13 Blade 13a Radial inner end 13b Axial upper end 13c Radial outer end 14 Shroud 14a Radial inner end 15 Main wing 16 Auxiliary Blade 20 Impeller case 20a Side end portion 20b Inner side surface 21 Motor case 21a Motor housing portion 21b Recessed portion 30 Motor 31 Shaft 32 Bearing 33 Rotor magnet 34 Stator 35 Bearing holding portion 40 Air inlet 50 Wind tunnel portion 100, 110 Centrifugal fan

Claims (13)

An impeller that rotates about a rotation axis;
An impeller case for housing the impeller;
A motor for rotationally driving the impeller;
A motor case coupled to the impeller case and containing the motor;
The impeller is
A boss coupled to a shaft that rotates coaxially with the rotational axis;
A hub extending radially outward from the outer peripheral surface of the boss portion;
A plurality of blades provided on the upper surface of the hub;
The plurality of blades extend radially outward from the rotation axis,
The inner wall of the impeller case that covers the plurality of blades has an inner surface that extends radially outward along the upper end portions of the plurality of blades,
The impeller case has an air inlet at the center, and a side end of the air inlet has a curved surface protruding radially inward ,
The plurality of blades have an upper axial end projecting upward at a radially outer side than a radially innermost end of the curved surface of the intake port,
The centrifugal fan in which the distance between the plurality of blades and the inner surface of the impeller case is the shortest at the axially upper ends of the plurality of blades .   An impeller that rotates about a rotation axis;
  An impeller case for housing the impeller;
  A motor for rotationally driving the impeller;
  A motor case coupled to the impeller case and containing the motor;
With
  The impeller is
    A boss coupled to a shaft that rotates coaxially with the rotational axis;
    A hub extending radially outward from the outer peripheral surface of the boss portion;
    A plurality of blades provided on the upper surface of the hub;
Have
  The plurality of blades extend radially outward from the rotation axis,
  The inner wall of the impeller case that covers the plurality of blades has an inner surface that extends radially outward along the upper end portions of the plurality of blades,
  The impeller case has an air inlet at the center, and a side end of the air inlet has a curved surface protruding radially inward,
  The plurality of blades have a radially outer end located on the most radially outer side of the upper end portion,
  The centrifugal fan in which the distance between the plurality of blades and the inner surface of the impeller case is the shortest at the radially outer ends of the plurality of blades. The centrifugal fan according to claim 1 or 2 , wherein an upper end portion of the boss portion is positioned below a radially innermost end of the curved surface of the intake port. 4. The centrifugal fan according to claim 1, wherein an upper end portion of the boss portion is located radially inward from a radially innermost end of a curved surface of the intake port. An upper surface of the hub, the centrifugal fan according to any one of the from the outer peripheral surface of the boss portion toward the lower side has an inclined surface inclined radially outward, claims 1 to 4.   The centrifugal fan according to any one of claims 1 to 5, wherein the plurality of blades, an inner wall of the impeller case, and the hub are inclined substantially in parallel. The centrifugal fan according to any one of claims 1 to 6 , wherein the inclined surface of the hub has a curved surface recessed radially inward and downward. The upper surface of the hub is
A flat surface extending substantially perpendicularly to the rotation axis from the radially outer end of the inclined surface,
The centrifugal fan according to any one of claims 1 to 7 , wherein a peripheral edge of the flat surface protrudes radially outward from peripheral edges of the plurality of blades. The centrifugal fan according to claim 8 , wherein the hub has an inclined surface inclined radially outward toward a lower side on a radially outer side of a peripheral edge of the flat surface. The centrifugal fan according to any one of claims 1 to 9 , wherein the curved surface of the intake port protrudes upward from the radially innermost end of the curved surface of the intake port. The centrifugal fan according to claim 10 , wherein an axial length of the curved surface of the intake port is smaller than a radial length. The plurality of blades are
A main wing extending from the radially inner side to the radially outer side than the radially innermost end of the curved surface of the intake port;
The centrifugal fan according to any one of claims 1 to 11 , further comprising an auxiliary wing extending from a radially outer side to a radially outer side than a radially innermost end of the curved surface of the intake port. An annular shroud is disposed at the upper ends of the plurality of blades,
The centrifugal fan according to any one of claims 1 to 12, wherein a radially inner end of the shroud is located radially outward from a radially outer end of the hub.

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