JP2018066346A - Blower and refrigerator provided with the same - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a centrifugal blower having two tongue portions, in which one wing passes near the radial inner side of one tongue portion and at the same time another wing passes near the radial inner side of another tongue portion. As it passes, noise is generated at the two tongues at the same time. The noise of this blower is suppressed. SOLUTION: An impeller 10 rotating around a central axis C and a housing 2 for accommodating the impeller to form a duct 5 are provided, the impeller has a plurality of blades 12, and the radial inner ends of the blades are blades. Arranged on the front side in the rotation direction of the impeller from the radial outer end of the housing, the housing has a tongue portion 25 between the impeller and a plurality of exhaust portions, respectively, and any two of the above blades are centered on a central axis. When the central angle formed by the radial outer end in the above is φ and the central angle formed by the recent contact point with the blade is θ in any two tongues, the central angle φ and the central angle θ are different. [Selection diagram] FIG. 9

Description

  The present invention relates to a blower device and a refrigerator including the same.

  A conventional blower is disclosed in Patent Document 1. This blower has a fan impeller that rotates around a central axis that extends in the front-rear direction, and a main casing that houses the fan impeller. An air suction port is provided in the center of the front side intake / blowout panel of the main body casing, and a pair of air blowout ports are provided on the left and right sides of the air suction port of the front side intake / blowout panel. The fan impeller includes a plurality of blades between the outer peripheral portion of the main plate and the annular shroud, and is configured by connecting the central portion of the main plate to the rotation shaft of the fan motor.

  The main body casing is provided with an air suction passage and an air blowing passage. The air suction passage extends from the air suction port toward the back panel of the main casing. The air outlet passage extends from the downstream side of the air suction passage to the air outlets on the left and right sides. Two tongue portions are provided at a position sandwiching the fan impeller in the air blowing passage.

  In the air blower configured as described above, when the fan impeller rotates, air flows into the main body casing through the air suction port. The air that has flowed into the main body casing flows between adjacent blades and accelerates radially outward along the blades. The air accelerated toward the outer side in the radial direction is blown out in the radial direction of the fan impeller, and is exhausted to the outside through the air outlet.

JP 2010-133623 A

  However, according to the blower disclosed in the above-mentioned patent document, one wing passes near the radially inner side of one tongue, and at the same time, the other wing passes near the radially inner side of the other tongue. To do. For this reason, there was a problem that noise was generated simultaneously at the two tongues, and the noise of the blower device was increased.

  An object of this invention is to provide the air blower which can reduce a noise, and a refrigerator provided with the same.

  An exemplary blower of the present invention is a blower, and includes an impeller that rotates around a central axis that extends vertically, and a casing that houses the impeller and forms a duct. A plurality of blades arranged in a circumferential direction of a central axis, wherein a radially inner end of the blade is disposed on a front side in a rotational direction of the impeller with respect to a radially outer end of the blade; Has an intake portion that covers the top of the impeller and penetrates in the axial direction, and a side surface of the housing covers a radially outer side of the impeller and penetrates in a direction perpendicular to the axial direction. The casing has a tongue portion between the impeller and the plurality of exhaust portions, and a center formed by radially outer ends of any two blades around the central axis. The angle is φ and any two of the above In part, upon the central angle formed by the closest point for said blades theta, and the central angle φ with said central angle theta is different.

  According to the exemplary present invention, it is possible to provide a blower capable of reducing noise and a refrigerator including the same.

FIG. 1 is a side sectional view of a refrigerator provided with a blower according to an embodiment of the present invention. FIG. 2 is a perspective view of the air blower according to the embodiment of the present invention. FIG. 3 is a plan view of the air blower according to the embodiment of the present invention. FIG. 4 is a side view of the air blower according to the embodiment of the present invention. FIG. 5 is a side cross-sectional view of the air blower according to the embodiment of the present invention. FIG. 6 is a bottom view of the blower according to the embodiment of the present invention. FIG. 7 is a view of the inside as viewed from the exhaust portion of the blower according to the embodiment of the present invention. FIG. 8 is a plan view of the inside of the air blower according to the embodiment of the present invention. FIG. 9 is an enlarged plan view in which a main part inside the blower according to the embodiment of the present invention is enlarged. FIG. 10 is an enlarged plan view showing an enlarged main part of the inside of the air blower according to the first modification of the embodiment of the present invention. FIG. 11 is an enlarged plan view showing an enlarged main part inside the blower according to the second modification of the embodiment of the present invention.

  Hereinafter, exemplary embodiments of the present invention will be described in detail with reference to the drawings. In this specification, in the blower device 1, the direction parallel to the central axis C of the blower device 1 is “axial direction”, the direction orthogonal to the central axis C of the blower device 1 is “radial direction”, and The direction along the arc centered on the central axis C is referred to as “circumferential direction”. Similarly, for the impeller 10, the directions that coincide with the axial direction, the radial direction, and the circumferential direction of the blower device 1 in the state of being incorporated in the blower device 1 are simply “axial direction”, “radial direction”, and “circumferential direction”, respectively. Called “direction”. Further, in the present specification, in the blower device 1, the shape and positional relationship of each part will be described with the axial direction being the vertical direction and the intake part 3 side of the housing 2 being the top with respect to the impeller 10. The vertical direction is simply a name used for explanation, and does not limit the actual positional relationship and direction.

  Further, in this specification, in the refrigerator 100, the side on which the doors 102a and 103a are provided is the front side, the side on which the cool air passages 131 and 132 are provided is the rear side, and the horizontal direction orthogonal to the front-rear direction is the left-right direction. Assuming that the direction toward the floor surface F is the downward direction and the direction away from the floor surface F is the upward direction, the shape and positional relationship of each part will be described. These directions are simply names used for explanation, and do not limit the actual positional relationship and direction.

<1. Overall configuration of refrigerator>
The refrigerator provided with the air blower of exemplary embodiment of this invention is demonstrated. FIG. 1 is a side sectional view of a refrigerator 100 provided with a blower 1 according to an embodiment of the present invention. The arrow S indicates the flow of cold air. The refrigerator 100 is installed on the floor surface F, and the refrigerator compartment 102 (storage room) opened and closed by the door 102a is arrange | positioned at the upper part of the refrigerator 100. FIG. Below the refrigerator compartment 102, a freezer compartment 103 (storage compartment) that is opened and closed by a door 103a is arranged.

  The refrigerator compartment 102 is maintained at a refrigerator temperature (for example, 3 ° C.) to store stored items in a refrigerator. In the refrigerator compartment 102, a plurality of trays 160 for placing stored items are provided. The door 102a of the refrigerator compartment 102 is provided with a plurality of storage pockets (not shown).

  The freezer compartment 103 is isolated from the refrigerator compartment 102 by the heat insulating wall 107 and is maintained below the freezing point to store the stored items in a frozen state. The freezer compartment 103 is provided with a plurality of storage cases 170 for storing stored items. The storage case 170 is supported to be movable in the front-rear direction by rails (not shown) provided on both side walls in the freezer compartment 103.

  A machine room 150 is provided behind the freezer room 103. A compressor 157 is disposed in the machine room 150. A condenser, an expander (all not shown) and a cooler 111 are connected to the compressor 157, and a refrigerant such as isobutane is circulated by driving the compressor 157 to operate a refrigeration cycle. Thereby, the cooler 111 becomes the low temperature side of the refrigeration cycle.

  A cool air passage 131 that is partitioned by a back plate 106 is provided behind the freezer compartment 103. A cold air passage 132 communicating with the cold air passage 131 is provided behind the refrigerator compartment 102. The cool air passage 131 is divided into a front portion 131a and a rear portion 131b by a partition plate 135, and a cooler 111 is disposed in the rear portion 131b. The cooler 111 on the low temperature side of the refrigeration cycle exchanges heat with the air flowing through the cool air passage 131 to generate cool air.

  The air blower 1 is disposed above the cooler 111 in the cold air passage 131. The blower 1 is a centrifugal blower that sucks air in the axial direction and exhausts it in the circumferential direction. The blower 1 is arranged with the two exhaust parts 4 (see also FIG. 2) facing the front lower side and the rear upper side, respectively.

  The cool air passage 131 opens a discharge port 109 in the partition plate 106 in front of the blower 1. Cold air is sent to the freezer compartment 103 through the discharge port 109 by driving the blower 1. A freezer compartment return port 122 is provided below the freezer compartment 103. The cold air flowing out of the freezer compartment 103 through the freezer return port 122 returns to the lower part of the cooler 111.

  A plurality of discharge ports 108 for discharging cool air are provided above the cool air passage 132. A return ventilation path (not shown) is led out from the lower part of the back surface of the refrigerator compartment 102. The return ventilation path is connected to the lower part of the cold air passage 131. The cold air flowing out of the refrigerator compartment 102 and passing through the return ventilation path returns to the lower side of the cooler 111.

<2. Operation of refrigerator>
In the refrigerator 1 having the above configuration, for example, when the temperature of the refrigerator compartment 102 becomes higher than the set temperature, the compressor 157 is driven. Thereby, the refrigeration cycle is operated, and cool air is generated by the cooler 111.

  The cool air generated by the cooler 111 is exhausted from the upper exhaust unit 4 and the lower exhaust unit 4 by driving the blower 1. The cold air exhausted from the lower exhaust unit 4 is sent to the freezer compartment 103 through the discharge port 109. The cold air sent to the freezer compartment 103 flows through the freezer compartment 103, flows out from the freezer compartment return port 122, and returns to the cooler 111. Thereby, the inside of the freezer compartment 103 is cooled.

  Further, the cold air sent from the upper exhaust unit 4 flows into the cold air passage 132. The cold air flowing through the cold air passage 132 is discharged from the discharge port 108 to the refrigerator compartment 102.

  The cold air discharged into the refrigerator compartment 102 flows forward on the tray 160 and exchanges heat with the stored items placed on the tray 160. And the stored thing in the storage pocket (not shown) provided in the door 102a cools, and flows downward.

  The cold air flowing through the refrigerator compartment 102 returns to the cooler 111 through a return ventilation path (not shown). Thereby, the inside of the refrigerator compartment 102 is cooled. When the temperature in the refrigerator compartment 102 becomes lower than the set temperature, the compressor 157 is stopped.

<3. Overall configuration of blower>
2 to 6 are a perspective view, a plan view, a side view, a side sectional view, and a bottom view, respectively, of the blower device 1. FIG. 7 is a view of the inside as viewed from the exhaust part 4 of the blower 1. The blower 1 has an impeller 10 and a motor 50 (see FIG. 3) in a housing 2.

  The housing 2 includes a cover portion 2a and a storage portion 2b. The cover portion 2a constituting the upper surface of the housing 2 is provided with an intake portion 3 penetrating in the axial direction. The air intake portion 3 has a cylindrical portion 32 that extends axially upward from the upper surface of the cover portion 2 a of the housing 2. Further, the cylinder portion 32 is provided with a bell mouth 31 which is bent inward from the upper end and extends downward (side of the storage portion 2b). As a result, the inner diameter of the intake portion 3 decreases smoothly from the upper side in the axial direction toward the lower side in the axial direction. The cover portion 2 a covers the top of the impeller 10 on the outer peripheral side of the intake portion 3.

  The opening part of the storage part 2b is covered with the cover part 2a. The storage portion 2 b stores the impeller 10 and the motor 50 that rotate about the central axis C that extends vertically, and the side surface of the storage portion 2 b covers the radially outer side of the impeller 10. A plurality of exhaust parts 4 are provided on the side surface of the storage part 2b. In the present embodiment, two exhaust parts 4 are provided. The exhaust part 4 penetrates the storage part 2b in a direction orthogonal to the axial direction, and is disposed on the side surfaces of the storage part 2b facing each other.

  The lower surface (bottom surface) of the storage portion 2b has a lower surface recess 2c that is recessed downward in the axial direction. The motor 50 is attached to the bottom surface of the lower surface recess 2c.

  The lower surface recess 2c has a mounting portion 15 (see FIG. 6) that is disposed below the blade 12 in the axial direction and expands in a direction orthogonal to the axial direction. That is, the attachment portion 15 is disposed in the lower surface recess 2c. The attachment portion 15 is provided with an insertion hole 15a through which a screw (not shown) for attachment to the refrigerator 1 is inserted. The blower 1 is attached to the refrigerator 1 via the attachment portion 15.

  Note that the air intake portion 3 may be provided on the bottom surface of the storage portion 2b instead of the cover portion 2a, and the motor 50 may be attached to the cover portion 2a. That is, the intake part 3 and the exhaust part 4 may be appropriately provided for the members constituting the housing 2.

  The casing 2 constitutes a duct 5 that connects the intake portion 3 and the plurality of exhaust portions 4, and the impeller 10 is disposed in the duct 5. The duct 5 has an intake passage 5a and a plurality of exhaust passages 5b. The intake passage 5 a connects the intake portion 3 and the impeller 10. The exhaust passage 5 b connects the downstream side of the impeller 10 and the exhaust part 4. The exhaust passage 5b extends in a direction orthogonal to the axial direction. The two exhaust passages 5b extend in opposite directions. That is, the two exhaust passages 5b are arranged on a straight line.

  The housing 2 has tongue portions 25 between the impeller 10 and the plurality of exhaust portions 4. That is, the duct 5 (exhaust passage 5 b) has a tongue portion 25 between the impeller 10 and each exhaust portion 4. In the present embodiment, two tongue portions 25 are provided. That is, the number of tongue portions 25 is an even number. The tongue 25 is disposed in the vicinity of the impeller 10. When the air blower 1 is driven as will be described later, the airflow A blown from the impeller 10 by the tongue portion 25 is smoothly guided to the exhaust passage 5b and the dynamic pressure is converted into a static pressure.

  That is, the blower 1 includes an impeller 10 that rotates around a central axis C that extends vertically, and a housing 2 that houses the impeller 10 and forms a duct 5. The impeller 10 has a plurality of blades 12 arranged in the circumferential direction of the central axis C. The upper surface of the housing 2 has an intake portion 3 that covers the top of the impeller 10 and penetrates in the axial direction. The side surface of the housing 2 has a plurality of exhaust parts 4 that cover the radially outer side of the impeller 10 and penetrate in a direction orthogonal to the axial direction. The housing 2 has tongue portions 25 between the impeller 10 and the plurality of exhaust portions 4.

<4. Impeller configuration>
The impeller 10 has a base plate 11 and a plurality of blades 12. In the present embodiment, ten blades 12 are provided. That is, the number of blades 12 is an even number. The base plate 11 is made of a resin molded product and has a circular shape when viewed from above. A protruding portion 11a is provided at the central portion of the base plate 11 so as to protrude upward in the axial direction (on the intake portion 3 side). As shown in FIG. 5, the upper surface of the protruding portion 11 a is disposed below the lower end of the bell mouth 31.

  The motor 50 attached to the lower surface recess 2c is disposed inside the protrusion 11a. A through hole (not shown) into which a shaft portion (not shown) of the motor 50 is press-fitted is provided at the center (on the center axis C) of the protruding portion 11a. Thereby, the protrusion part 11a and the axial part 50a are connected, and the base plate 11 is supported rotatably about the central axis C. As will be described later, the base plate 11 rotates in the rotation direction R (clockwise as viewed from the top in FIG. 3) by driving the motor 50.

  The plurality of blades 12 are integrally formed with the base plate 11 and are arranged on the base plate 11 at a predetermined interval in the circumferential direction of the central axis C.

  A radius D1 (see FIG. 3) of the inner diameter of the intake section 3 is larger than a distance D2 (see FIG. 3) between the radial inner ends of the plurality of blades 12 and the central axis C. In FIG. 3, the radially inner ends of the plurality of blades 12 are all at the same distance from the central axis C, and thus are on a circle K (indicated by a dashed line in FIG. 3) centered on the central axis C. To position. For this reason, the distance D2 between the radially inner ends of the plurality of blades 12 and the central axis C may be regarded as the radius of a circle K passing through the radially inner ends of the plurality of blades 12. Further, the upper ends in the axial direction of the plurality of blades 12 are housed inside the cylindrical portion 32 in the radial direction, and are disposed axially above the upper surface of the cover portion 2a of the housing 2 as shown in FIG.

  Further, the upper portions of the plurality of blades 12 are connected to each other by an annular ring portion 13 (see FIG. 5) that is located on the radially outer side and that has the central axis C as the center. That is, the impeller 10 has an annular ring portion 13 that is connected to at least a part of the upper portion of the adjacent blade 12. The ring portion 13 is formed integrally with the blade 12. The ring portion 13 can improve the rigidity of the blade 12.

<5. Relationship between blade and tongue>
FIG. 8 is a plan view of the inside of the blower 1. FIG. 9 is an enlarged plan view in which a main part inside the blower 1 is enlarged. The inner end in the radial direction of the blade 12 is disposed on the front side in the rotational direction R of the impeller 10 with respect to the outer end in the radial direction of the blade 12. That is, the inner peripheral end of the blade 12 is disposed in front of the outer peripheral end in the rotational direction R. Thereby, the blade 12 is inclined with respect to the radial direction.

  In addition, the radially inner end of one blade 12 is disposed closer to the front side in the rotational direction R of the impeller 10 than the radially outer end of the other blade 12 adjacent to the forward side in the rotational direction R of the impeller 10 than the blade 12. Is done.

  The radially outer ends of the plurality of blades 12 are arranged at equal intervals in the circumferential direction. Thereby, the balance of the rotating impeller 10 can be improved.

  When the central angle formed by the radially outer ends of any two blades 12 around the central axis C is φ, and the central angle formed by the closest contact CP with respect to the blades 12 at any two tongues 25 is θ Further, the central angle φ and the central angle θ are different. That is, the central angle φ formed by the radially outer ends of any two blades 12 around the central axis C is all different from the central angle θ. The central angle φ is m × 36 ° (m is an integer of 1 to 5), and the central angle θ is smaller than 180 °.

  Further, the cross-sectional area W1 of the flow path intersecting with one tongue 25 and orthogonal to the air flow A in the duct 5 and the other tongue 25 different from the one tongue 25 intersect with the air flow in the duct 5. The cross-sectional area W2 of the flow path orthogonal to A is substantially the same.

<6. Operation of the blower>
When the temperature in the refrigerator compartment 102 becomes higher than the set temperature and the compressor 157 of the refrigerator 100 is driven, the motor 50 of the blower 1 is driven. When the motor 50 is driven, the impeller 10 rotates about the central axis C. Thereby, air (cold air) is taken into the housing 2 from the intake portion 3.

  The air taken into the housing 2 passes between the adjacent blades 12 and is accelerated radially outward by the rotating impeller 10. The air accelerated toward the outer side in the radial direction flows between the adjacent blades 12 between the ring portion 13 and the base plate 11 and is blown out radially outward of the impeller 10. The air blown outward in the radial direction of the impeller 10 flows through the duct 5 (exhaust passage 5b) and is exhausted from the exhaust unit 4 to the outside of the housing 2.

  At this time, since the central angle φ and the central angle θ are different, it is possible to prevent the plurality of blades 12 from passing in the vicinity of the radially inner side of the plurality of tongue portions 25 at the same time. Therefore, simultaneous generation of noise at the two tongue portions 25 can be prevented, and the noise of the blower 1 can be reduced.

  When the number of tongues 25 is 2 and the number n of blades 12 is an even number, if the central angle θ satisfies 180 ° -360 ° / n <θ <180 °, the noise of the blower 1 The flow path width of the duct 5 (exhaust passage 5b) can be increased while reducing the above. The number n of the blades 12 is not limited to 10 and may be an even number.

<5. First Modification>
As shown in FIG. 10, the number of tongues 25 of the blower 1 may be two, the number of blades 12 may be eleven (odd number), and the center angle θ may be 180 °. Also in this case, since the central angle θ and the central angle φ are different, the simultaneous generation of noise at the two tongue portions 25 can be prevented, and the noise of the blower 1 can be reduced. Moreover, since the number of the blades 12 and the number of the tongue portions 25 are relatively prime, a reduction in the degree of freedom in designing the duct 5 can be reduced. That is, if the number of the blades 12 and the number of the tongue portions 25 are relatively prime, the radially outer ends of the plurality of blades 12 are arranged at equal intervals in the circumferential direction and the plurality of tongue portions 25 are equally spaced in the circumferential direction. Even if it arrange | positions in this, it can prevent that the several braid | blade 12 passes simultaneously the radial inner side vicinity of the some tongue part 25 simultaneously. Furthermore, since the central angle θ is 180 °, the flow passage width of the two exhaust passages 5b can be increased. The number of blades 12 is not limited to 11 and may be an odd number.

<6. Second Modification>
Moreover, as shown in FIG. 11, while the number of the tongue parts 25 is three (odd number), the number n of the blades 12 may be ten (even number). The three exhaust passages 5b are radially arranged at substantially equal intervals. In any two tongues 25, when the central angle formed by the closest point CP to the blade 12 is θ, the central angle φ and the central angle θ are different. Also in this case, simultaneous generation of noise at the three tongue portions 25 can be prevented, and the noise of the blower 1 can be reduced. In addition, the number of the tongue parts 25 is not limited to three, What is necessary is just three or more odd numbers. Further, the number n of the blades 12 is not limited to 10 and may be an even number. When the number of the tongue portions 25 is three and the central angle θ satisfies 120 ° -360 ° / n <θ <120 °, the flow passage width of the three exhaust passages 5b can be increased.

  According to the present embodiment, the central angle formed by the radially outer ends of any two blades 12 around the central axis C is φ, and the center where the closest point CP to the blade 12 is formed at any two tongues 25 When the angle is θ, the central angle φ and the central angle θ are different. Thereby, it can prevent that the several braid | blade 12 passes simultaneously the radial direction inner side vicinity of the some tongue part 25 at the same time. Therefore, simultaneous generation of noise at the plurality of tongue portions 25 can be prevented, and noise of the blower 1 can be reduced. In addition, the number of the tongue parts 25 and the blades 12 should just be plural.

  The radially outer ends of the plurality of blades 12 are arranged at equal intervals in the circumferential direction. Thereby, the balance at the time of rotation of the impeller 10 can be improved.

  Moreover, when the number of the blades 12 and the number of the tongue portions 25 are relatively prime, a reduction in the degree of freedom in designing the duct 5 can be reduced.

  At this time, when the central angle θ is 180 °, the flow path width of the duct 5 (exhaust passage 5b) on the downstream side of the impeller 10 can be increased. Therefore, the blowing efficiency of the blower 1 can be improved.

  When the number of tongues 25 is an even number, the number of blades 12 is an odd number, and the central angle θ is 180 °, the flow path width of the duct 5 (exhaust passage 5b) on the downstream side of the impeller 10 is increased. can do. Therefore, the blowing efficiency of the blower 1 can be improved.

  Further, when the number of tongues 25 is 2 and the number n of blades 12 is an even number, if the central angle θ satisfies 180 ° -360 ° / n <θ <180 °, the duct 5 (exhaust passage) The flow path width of 5b) can be increased.

  Further, when the number of tongues 25 is 3 and the number n of blades 12 is an even number, if the central angle θ satisfies 120 ° -360 ° / n <θ <120 °, air is blown in three directions. Even in the case of delivery, the flow path width of the duct 5 (exhaust passage 5b) can be increased.

  Further, the cross-sectional area W1 of the flow path intersecting with one tongue 25 and orthogonal to the air flow A in the duct 5 and the other tongue 25 different from the one tongue 25 intersect with the air flow in the duct 5. The cross-sectional area W2 of the flow path orthogonal to A is substantially the same. Thereby, the air volume of the airflow which distribute | circulates the several exhaust passage 5b (duct 5) can be made uniform, and ventilation efficiency can be improved.

  Further, the inner end in the radial direction of one blade 12 is closer to the front side in the rotational direction R of the impeller 10 than the outer end in the radial direction of the other blade 12 adjacent to the front side in the rotational direction R of the impeller 10 than the one blade 12. Placed in. As a result, the inner end of one blade 12 and the outer end of another blade 12 adjacent to the blade 12 can be prevented from passing through the radially inner side of the tongue portion 25 at the same time. Therefore, the noise of the blower 1 can be further reduced.

  The radius D1 of the inner diameter of the intake portion 3 is greater than the distance D2 between the radial inner ends of the plurality of blades 12 and the central axis C. Thereby, the distance of the radial direction inner end and radial direction outer end of the braid | blade 12 which opposes the air intake part 3 can be enlarged. Therefore, it is possible to increase the area of the blade 12 facing the intake portion 3 and to take in a large amount of air from the intake portion 3 into the housing 2. Therefore, the blowing efficiency of the blower 1 can be improved.

  Further, the upper portions of the plurality of blades 12 are connected by an annular ring portion 13 centering on the central axis C. Thereby, the rigidity of the blade 12 can be improved. Therefore, vibration of the blade 12 when the impeller 10 rotates can be suppressed. As a result, the noise of the blower 1 can be further reduced.

  Further, the inner diameter of the intake portion 3 is smoothly reduced from the upper side in the axial direction toward the lower side in the axial direction. Thereby, the air sucked from the intake portion 3 can be rectified and smoothly guided between the adjacent blades 12. Therefore, the intake efficiency of the blower 1 can be improved.

  Further, the intake portion 3 has a cylindrical portion 32 that extends upward in the axial direction from the upper surface of the housing 2. The upper ends in the axial direction of the plurality of blades 12 are housed inside the cylindrical portion 32 in the radial direction, and are disposed above the upper surface of the housing 2 in the axial direction. As a result, the length of the blade 12 in the axial direction can be increased, the area of the blade 12 can be increased, and a large amount of air can be taken in from the intake portion 3. Therefore, the blowing efficiency of the blower 1 can be improved.

  The housing 2 has an attachment portion 15 that is disposed below the blade 12 in the axial direction and extends in a direction orthogonal to the axial direction, and the lower surface of the housing 2 has a lower surface recess 2c that is recessed downward in the axial direction. . And the attaching part 15 is arrange | positioned in the lower surface recessed part 2c. As a result, the length of the blade 12 in the axial direction can be increased, and the area of the blade 12 can be increased to take in more air from the intake section 3. Therefore, the blowing efficiency of the blower 1 can be further improved.

  The refrigerator 100 includes the blower 1. Thereby, the refrigerator which can reduce noise is easily realizable.

  The refrigerator 100 includes a refrigerator compartment 102 (storage compartment) and a freezer compartment 103 (storage compartment) for storing stored items in a cold state, a cooler 111 for generating cold air, a refrigerator compartment 102, a freezer compartment 103, and a cooler 111. And cold air passages 131 and 132 that communicate with each other. The blower 1 is disposed in the cold air passage 131. Thereby, cold air can be guided to the refrigerator compartment 102 and the freezer compartment 103 while reducing noise. Note that the storage room may be only one of the refrigerator compartment 102 and the freezer compartment 103.

  In addition, in this embodiment, although the air blower 1 is mounted in the refrigerator 100, even if the air blower 1 is mounted in various OA equipment, medical equipment, transport equipment, household electric appliances other than the refrigerator 100, etc. Good.

  According to this invention, it can utilize for an air blower and a refrigerator provided with the same.

  DESCRIPTION OF SYMBOLS 1 ... Air blower, 2 ... Housing, 2a ... Cover part, 2b ... Storage part, 2c ... Lower surface recessed part, 3 ... Intake part, 4 ... Exhaust part, 5 ... Duct, 5a ... Intake passage, 5b ... Exhaust passage, 10 ... Impeller, 11 ... Base plate, 11a ... Projection, 12 ... Blade, 15 ... Mounting portion 25 ... tongue, 31 ... bell mouth, 32 ... tube, 100 ... refrigerator, 102 ... refrigerator compartment (storage room), 102a ... door, 103 ... frozen Chamber (storage chamber), 103a ... door, 106 ... back plate, 107 ... heat insulation wall, 108 ... discharge port, 109 ... discharge port, 111 ... cooler, 122 ... -Freezer return port, 131 ... cold air passage, 132 ... cold air passage, 150 ... machine room, 157 ... compressor, 16 ... Tray, 170 ... Storage case, A ... Airflow, C ... Center axis, CP ... Closest point, D1 ... Radius, D2 ... Distance, S ... Arrow, R: rotational direction, θ: central angle, φ: central angle, W1: cross-sectional area, W2: cross-sectional area

Claims (16)

A blower,
An impeller rotating around a central axis extending vertically;
A housing that houses the impeller and forms a duct;
With
The impeller has a plurality of blades arranged in a circumferential direction of the central axis,
The radially inner end of the blade is disposed on the front side in the rotational direction of the impeller from the radially outer end of the blade,
The upper surface of the housing has an intake portion that covers the top of the impeller and penetrates in the axial direction,
The side surface of the housing has a plurality of exhaust portions that cover the radially outer side of the impeller and penetrate in a direction perpendicular to the axial direction,
The housing has tongue portions between the impeller and the plurality of exhaust portions, respectively.
Centering on the central axis,
The central angle formed by the radially outer ends of any two of the blades is φ,
In any two of the tongues, when the central angle formed by the closest point to the blade is θ,
The air blower in which the central angle φ and the central angle θ are different.   The air blower according to claim 1, wherein the radially outer ends of the plurality of blades are arranged at equal intervals in the circumferential direction.   The blower according to claim 1 or 2, wherein the number of the blades and the number of the tongue portions are relatively prime.   The air blower according to claim 3, wherein the central angle θ is 180 °.   The blower device according to claim 4, wherein the number of tongue portions is an even number, the number of blades is an odd number, and the central angle θ is 180 °.   The center angle θ satisfies 180 ° -360 ° / n <θ <180 ° when the number of the tongues is 2 and the number n of the blades is an even number. The blower described in 1.   The center angle θ satisfies 120 ° -360 ° / n <θ <120 ° when the number of the tongues is 3 and the number n of the blades is an even number. The air blower in any one of.   A cross-sectional area of a flow path intersecting with one tongue and perpendicular to the air flow in the duct, and a flow intersecting with another tongue different from the one tongue and perpendicular to the air flow in the duct The air blower according to any one of claims 1 to 7, wherein the cross-sectional area of the road is substantially the same.   The radially inner end of one blade is arranged on the front side in the rotational direction of the impeller from the radial outer end of the other blade adjacent to the forward side in the rotational direction of the impeller than the one blade. The air blower according to any one of claims 1 to 8.   The blower according to any one of claims 1 to 9, wherein a radius of an inner diameter of the intake portion is larger than a distance between a radially inner end of the plurality of blades and the central axis.   The air blower according to any one of claims 1 to 10, wherein upper portions of the plurality of blades are connected by an annular ring portion centered on the central axis.   The air blower according to any one of claims 1 to 11, wherein an inner diameter of the intake portion is smoothly reduced from an upper side in the axial direction toward a lower side in the axial direction. The intake portion has a cylindrical portion extending axially upward from the upper surface of the housing,
The axial upper ends of the plurality of blades are housed inside in the radial direction of the cylindrical portion, and are disposed axially above the upper surface of the casing. apparatus. The housing has an attachment portion that is disposed below the blade in the axial direction and extends in a direction perpendicular to the axial direction,
The lower surface of the housing has a lower surface recess that is recessed downward in the axial direction.
The blower device according to claim 1, wherein the attachment portion is disposed in the lower surface recess.   A refrigerator provided with the air blower in any one of Claims 1-14. A storage room for storing the stored product in a cold state, a cooler for generating cold air, and a cold air passage for communicating the storage room and the cooler,
The refrigerator according to claim 15, wherein the blower is disposed in the cold air passage.