JP2006105156A - Impeller, blower, and refrigerator - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To prevent separation of an air flow, and restrict turbulence in a confluent flow in the condition of high air way resistance wherein speed increase of an axially discharged air flow from a pressure surface side trailing edge of a blade generates a large circulation vortex at a suction side leading part of the blade, separates an air flow along a negative pressure surface by a suction, turbulent air flow enlarges turbulence when the pressure surface side air flow is confluent with the negative pressure surface side one at the trailing edge, deteriorates blowing performance of an impeller, and increases generated turbulence sound. <P>SOLUTION: A recessed part (air flow direction changing means) 8b extended to be close to the trailing edge of the blade 8 at one end is provided on the side of a pressure surface 5 of the blade 8, and a protruded part 8a (air flow adhering means) is provided at a trailing edge part of the blade 8. An air flow of a large radial speed component passing the impeller 9 is converted into an axial direction by the recessed part 8b to increase air flow speed in the axial direction, and separation of the negative surface side air flow is restricted by the protruded part 8a. Turbulence occurring when the air flow on the negative surface side is confluent with the air flow on the pressure surface side can thus be restricted, thereby deterioration of blowing performance of the impeller and increase of blowing noise can be restricted. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to a blower used in a refrigerator, an air conditioner, an OA device, or the like.

  In recent years, axial blowers are mounted on refrigerators, air conditioners, office automation equipment, and the like and are widely used, and there is a tendency for downsizing, high density, high performance, and low noise.

  As a conventional axial blower, for example, the one shown in Patent Document 1 is known.

  Hereinafter, the above-described conventional axial blower will be described with reference to the drawings.

  22 to 25 are conventional axial-flow impellers, FIG. 22 is a front view of the impeller, FIG. 23 is a sectional view taken along line xx of FIG. 22, and FIG. FIG. 25 is a front view, and FIG. 25 is a sectional view taken along line yy of FIG.

  22 and 23, reference numeral 1 denotes an impeller, which includes a hub 3 attached to the motor 2 and a plurality of blades 4 provided around the hub 3. The protrusion 6 that protrudes toward the pressure surface 5 from the front edge 4a to the rear edge 4b of the blade 4 is located on the outer peripheral side with a curvature. In FIG. 22, the front edge 4a of the blade 4 is positioned in front of the drawing from the rear edge 4b, and the impeller 1 has a structure in which air is blown out to the back side by left rotation indicated by an arrow.

The operation of the impeller configured as described above will be described below. First, when the impeller 1 rotates at a predetermined rotational speed from the motor 2, air flows into the impeller 1, static pressure and dynamic pressure are added by the action of the impeller 4, and the air is discharged out of the impeller 1 and blown. To work. By providing the protrusion 6 on the pressure surface 5 side of the blade 4, the leakage flow from the pressure surface 5 to the negative pressure surface 7 is first accelerated at the protrusion start portion, from the axial center side to the blade outer periphery along the blade pressure surface. The noise generation factor is reduced by reducing the fluctuation flow component included in the flowing main flow. That is, by creating a leakage flow from the pressure surface to the suction surface, pressure fluctuations at the outer peripheral end (pressure difference between the pressure surface and the suction surface) are reduced, and an increase in noise is suppressed.
Japanese Patent Laid-Open No. 11-44432

  However, in the configuration as described above, when the impeller 1 is used under conditions of high air path resistance such as in a refrigerator, the airflow passing through the pressure surface 5 side of the blade 4 is a radial component as shown in FIG. The air current A is strong. The airflow having a strong radial component is blocked by the protrusion 6 provided on the pressure surface 5 side of the blade 4 and converted into the axial direction, and is discharged from the trailing edge of the blade 4. Therefore, the discharge air velocity in the axial direction from the rear edge on the pressure surface 5 side increases. In addition, since a large circulating vortex (not shown) is generated at the tip of the blade 4 on the suction side under a condition where the air path resistance is high, the airflow sucked into the impeller 1 is disturbed and the airflow along the suction surface 7 Causes delamination. That is, when the airflow between the pressure surface 5 side and the negative pressure surface 7 side at the trailing edge merges, the speed difference increases and the turbulence increases. Therefore, the ventilation performance of the impeller 1 is deteriorated, and there is a problem that the turbulent sound generated increases.

  The present invention provides an impeller, a blower using the impeller, and a refrigerator / refrigerator using the blower provided with an airflow having a large radial component passing through the impeller under a high airflow resistance condition on the pressure surface side. The airflow direction conversion means such as a concave portion is converted into the axial direction, a convex portion is provided as an airflow adhesion means at the trailing edge of the blade, and the chord length is partially increased, so that the airflow direction conversion means axially The airflow converted into airflow flows in the vicinity of the airflow attachment means to suppress separation of the airflow on the suction side, and to suppress turbulence that occurs when the airflow on the pressure surface side and airflow on the suction surface side merge at the trailing edge Thus, it is an object to suppress deterioration of the blowing performance of the impeller and to suppress an increase in blowing noise.

  The impeller according to claim 1 of the present invention includes a hub attached to a motor and a plurality of blades provided around the hub, and is sucked into the blade provided on the pressure surface side of the blade. An airflow direction converting means for converting the generated airflow into an axial direction, and an airflow to which a separation flow provided in the rear edge of the blade is attached in the vicinity of the flow of the airflow converted in the axial direction by the airflow direction converting means It is characterized by having an attachment means for each of the plurality of blades, such as when the impeller is installed or when the airflow resistance is high due to the configuration of the product airway. An airflow having a large radial velocity component passing through the vehicle is converted into an axial direction by an airflow direction converting means provided on the pressure surface side, and an axial airflow velocity discharged from the pressure surface side is increased, and the trailing edge of the blade Airflow adhering means is provided on the The airflow converted in the axial direction by the direction changing means flows in the vicinity of the airflow attaching means to suppress separation of the airflow on the suction surface side, and the airflow blown from the suction surface side and the airflow discharged from the pressure surface side By suppressing the turbulence that occurs at the time of merging, the air blowing performance of the impeller is suppressed, and the increase in blowing noise is suppressed.

  The invention of the impeller described in claim 2 is characterized in that, in the invention described in claim 1, the position of the airflow direction changing means extends to the position of the airflow attaching means. An axial airflow converted into the axial direction and discharged from the pressure surface, and an airflow adhering means provided at the trailing edge of the blade suppresses separation of the airflow on the suction surface side, and an airflow blown from the suction surface side, Are combined at the same position, and the disturbance generated at the time of merging is further suppressed, so that deterioration of the blowing performance of the impeller can be suppressed and increase in blowing noise can be suppressed.

  The invention of the blower according to claim 3 is the impeller of the invention according to claim 1, and the invention of the blower according to claim 4 is the impeller of the invention according to claim 2, each of which is an outer periphery of the impeller. The first and second plate-like mouth rings that define the suction side and the discharge side, the outer wall surrounding the outer circumference of the first and second plate-like mouth rings, A swirl flow circulation space having an opening facing the blades of the impeller between the second plate-shaped mouth rings, and the opening of the impeller from the opening edges of the first and second plate-shaped mouth rings. There are a plurality of pillars extending substantially in the radial direction, and a part of the airflow having a large radial velocity component passing through the impeller is provided on the outer periphery of the impeller from the pressure surface side of the impeller. Is sucked into the swirling flow circulation space, and the blades in the swirling flow circulation space The swirl flow swirling in the rotational direction with a strong circumferential component due to the action, but swirling of swirl flow is blocked by a plurality of columns provided extending from the opening edge in the substantially radial direction of the impeller, and swirl flow circulation By discharging from the space to the low pressure part on the suction surface side of the blade, the speed of the airflow flowing along the suction surface side is increased, so that turbulence that occurs at the time of merging with the discharge airflow from the pressure surface side can be suppressed. . In addition, a part of the airflow passing through the impeller is sucked and exhausted in the swirl circulation space and discharged again to the discharge side, thereby suppressing the deterioration of the blowing performance of the impeller and suppressing the increase of blowing noise. Have

  The invention of the refrigerator according to claim 5 uses the blower of the invention according to claim 3 in an air passage that supplies cooling air to a storage chamber in the refrigerator, and suppresses deterioration of blowing performance as a blower. This has the effect of improving the cooling capacity.

  The invention of the refrigerator according to claim 6 uses the blower of the invention of claim 3 in an air passage that supplies air into the machine room of the refrigerator, and suppresses deterioration of the blowing performance as a blower. , Has the effect of improving the condensation capacity.

  The invention of the refrigerator according to claim 7 uses the blower of the invention according to claim 4 in the refrigerator-freezer according to claim 5 or 6, and is converted into the axial direction by the airflow direction changing means and discharged from the pressure surface. The airflow in the axial direction and the airflow adhering means provided at the trailing edge of the blades suppress the separation of the airflow on the suction surface side, and the airflow blown out from the suction surface side is merged at the same position, and more merged By suppressing the turbulence that sometimes occurs, the air blowing performance of the impeller is suppressed, and the increase in blowing noise is suppressed.

  The invention according to claim 1 of the present invention includes a hub attached to a motor, and a plurality of blades provided around the hub, and an air flow sucked into the blade provided on the pressure surface side of the blade. An airflow direction converting means for converting the airflow into an axial direction, and an airflow attaching means for adhering a separation flow provided in the trailing edge of the blade in the vicinity where the airflow converted in the axial direction by the airflow direction converting means flows. For each of the plurality of blades, and it passes through the impeller when the impeller is installed or when the air flow resistance is high due to the configuration of the product air passage. Airflow with a large radial velocity component is converted to the axial direction by the airflow direction conversion means provided on the pressure surface side, and the axial airflow velocity discharged from the pressure surface side increases, and airflow adheres to the trailing edge of the blade. Means to change the direction of airflow When the airflow converted in the axial direction by the means flows in the vicinity of the airflow adhesion means, separation of the airflow on the suction surface side is suppressed, and when the airflow blown from the suction surface side and the airflow discharged from the pressure surface side merge By suppressing the generated turbulence, the effect of suppressing the deterioration of the blowing performance of the impeller and suppressing the increase of blowing noise can be obtained.

  Further, the invention according to claim 2 is characterized in that, in addition to the invention according to claim 1, the position of the airflow direction changing means extends to the position of the airflow attaching means. The axial airflow converted into the axial direction by the pressure surface and discharged from the pressure surface and the airflow blown out from the suction surface side by suppressing the separation of the airflow on the suction surface side by the airflow adhesion means provided at the trailing edge of the blade, Are combined at the same position, and the turbulence generated at the time of merging is further suppressed, so that deterioration of the blowing performance of the impeller can be suppressed and increase in blowing noise can be suppressed.

  In addition to the invention described in claim 1, the invention described in claim 3 is added to the invention described in claim 2, and in addition to the invention described in claim 2, the configuration of the orifice surrounding the outer periphery of the blade is the suction side. A first and second plate-like mouth ring that partitions the discharge side, an outer wall surrounding an outer periphery of the first and second plate-like mouth rings, and the first and second plate-like mouth rings A swirl flow circulation space having an opening facing the blades of the impeller, and extending from the opening edge of the first and second plate-like mouth rings in a substantially radial direction of the impeller. By providing a blower using the impeller of the present invention having a plurality of pillars, a part of the airflow having a large radial velocity component passing through the impeller is transferred from the pressure surface side of the blade to the outer periphery of the impeller. The action of the blade in the swirl flow circulation space is sucked into the swirl flow circulation space The swirl flow swirling in the direction of rotation with a strong circumferential component, but swirling of swirl flow is prevented by a plurality of columns provided extending substantially in the radial direction of the impeller from the opening edge, and in the swirl flow circulation space Since the speed of the airflow flowing along the suction surface side is increased by discharging to the low pressure portion on the suction surface side of the blade, the turbulence that occurs at the time of merging with the discharge airflow from the pressure surface side can be suppressed. In addition, a part of the airflow passing through the impeller is sucked and exhausted in the swirl circulation space and discharged again to the discharge side, thereby suppressing the deterioration of the blowing performance of the impeller and suppressing the increase of blowing noise. Is obtained.

  Moreover, in order to suppress the deterioration of the ventilation performance as an air blower by making into the refrigerator which used the air blower of this invention in the air path which supplies cooling air to the storage chamber in a refrigerator, invention of Claim 5 is cooling. The effect that ability improves is acquired.

  Further, the invention according to claim 6 has a condensing capacity in order to suppress the deterioration of the aerodynamic performance as the blower by using the blower of the present invention in the air passage that supplies air into the machine room of the refrigerator. The effect of improving is acquired.

  Further, the invention according to claim 7 is the invention according to claim 5 or 6, in addition to the invention according to claim 5 or 6, wherein the airflow is changed in the axial direction by the airflow direction changing means and discharged from the pressure surface, and the trailing edge of the blade The airflow adhesion means provided on the suction surface suppresses the separation of the airflow on the suction surface side, and the airflow blown out from the suction surface side merges at the same position, thereby suppressing the turbulence that occurs at the time of merging, The deterioration of the blowing performance can be suppressed, and the increase in blowing noise can be suppressed.

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

  In addition, about the part of the same structure as the past, the same code | symbol is attached | subjected and description is abbreviate | omitted.

(Embodiment 1)
FIGS. 1-15 shows the impeller of Embodiment 1 of this invention. 1 and 2, reference numeral 8 denotes a plurality of blades provided around the hub 3, and a convex portion (air flow adhesion means) 8 a is provided at the rear edge portion of the blade 8, and a concave portion (air flow direction conversion) The means 8b is provided on the pressure surface 5 side of the blade 8 and one end of the recess 8b extends to the vicinity of the rear edge of the blade 8. In FIG. 1, air is blown out to the back side by rotation in the direction indicated by the arrow.

  With this configuration, when the impeller 9 is installed and the configuration of the product air passage, when the air passage resistance is high as in the refrigerator, the blade 8 passes as shown in FIG. The airflow B having a large radial velocity component is blocked by the recess 8b and converted into the axial direction (downward in FIG. 4). Therefore, the airflow velocity in the axial direction discharged from the pressure surface 5 side increases. Further, as shown in FIG. 6, the air flow C that has been peeled off on the suction surface 7 side of the related art is provided with a convex portion 8a at the rear edge portion of the blade 8, and by partially increasing the chord length, It adheres like the airflow D in the vicinity of the trailing edge, and the separation of the airflow can be suppressed. Therefore, the turbulence generated when the airflow D blown from the negative pressure surface 7 side and the airflow E discharged from the pressure surface 5 side can be suppressed, deterioration of the air blowing performance of the impeller 9 can be suppressed, An increase in noise can be suppressed.

  Therefore, as shown in FIG. 8 by comparing the aerodynamic (PQ) characteristics of the impeller of this embodiment and the conventional impeller, the impeller of this embodiment has a higher static pressure than the conventional impeller. Suppressing the decrease in air volume under the conditions can be sufficiently achieved.

  Here, it is conceivable to extend the entire trailing edge of the blade 8 in order to suppress separation of the airflow, but in that case, the weight of the entire impeller increases and the load on the motor also increases, so the input increases. However, if the convex portion 8a is provided on a part of the rear edge portion as in the present invention, the separation of the airflow is suppressed without increasing the weight of the impeller and increasing the load on the motor. Can do.

  In this embodiment, the concave portion 8b is provided on the pressure surface 5 side. However, as shown in FIG. 5, in order to make the thickness of the blade 8 uniform, the concave portion 8b is negatively aligned with the concave portion 8b provided on the pressure surface 5 side. The same effect can be obtained by providing the convex portion 8d on the pressure surface 7 side.

  Further, in the present embodiment, the shape of the convex portion 8a provided on the trailing edge of the blade 8 is substantially arcuate, but as shown in FIGS. 9 to 11, the substantially triangular convex portion and the substantially triangular apex are formed. The same effect can be obtained by using a convex portion having an arc shape and two substantially arc-shaped convex portions having apexes.

  Further, in this embodiment, the positions of the concave portion 8b provided on the pressure surface 5 side and the convex portion 8a provided on the rear edge portion of the blade 8 are not limited, but as shown in FIG. When the distance from the outer peripheral edge of the blade 8 is DZ, as shown in FIG. 13, when the center position DM of the convex portion 8a is from about 0.5DZ to near the outer periphery 0.9Z, a large rotation near the outer periphery of the blade 8 Due to the energy, the airflow velocity in the axial direction converted by the concave portion 8b also increases, and the peripheral velocity of the blade 8 near the outer periphery is also fast, so the velocity of the airflow D adhering near the trailing edge by the convex portion 8a of the blade 8 is also high. By increasing the speed, a greater effect can be obtained.

  In the present embodiment, the size of the convex portion 8a provided on the trailing edge of the blade 8 is not limited. However, as shown in FIG. 14, the base DT of the convex portion 8a is from about 0.1 DZ to about 0.9 DZ. A great effect can be obtained in the above range. Further, as shown in FIG. 15, a great effect can be obtained when the height H of the convex portion 8a is in the range from about 0.2 DZ to about DZ. Further, for example, in the range where the center position DM of the convex portion 8a is near 0.7DZ to about 0.8DZ and the base DT of the convex portion 8a is near 0.4DZ to about 0.8DZ, the height H of the convex portion 8a. It has been confirmed that the maximum effect can be obtained when the value is near 0.1 to 0.35. Further, when the center position DM of the convex portion 8a is in another range, the same effect can be obtained by designing the base DT of the convex portion 8a with the length DT and the height H of the convex portion 8a appropriately taken into consideration.

(Embodiment 2)
FIG. 16 shows an impeller according to Embodiment 2 of the present invention. In addition, about the part of the same structure as Embodiment 1, the same code | symbol is attached and description is abbreviate | omitted.

  In FIG. 16, one end of the concave portion 8 b provided on the blade 8 extends to the tip of the convex portion 8 a provided on the blade 8.

  With this configuration, the air flow F having a large radial velocity component passing through the impeller 9 is blocked by the concave portion 8b provided on the pressure surface 5 side, converted into the axial direction, and the axial air flow discharged from the pressure surface 5 side. The protrusion 8a is provided at the rear edge of the blade 8, and the airflow D on the suction surface 7 side is suppressed by partially increasing the chord length, and the airflow blown out from the suction surface 7 side is By merging at the same position and suppressing the turbulence that occurs at the time of merging, it is possible to suppress the deterioration of the blowing performance of the impeller 9 and to suppress the increase in blowing noise.

(Embodiment 3)
FIGS. 17-20 shows the air blower of Embodiment 3 of this invention. In addition, about the part of the same structure as Embodiment 1, Embodiment 2, the same code | symbol is attached | subjected and description is abbreviate | omitted.

  17 and 18, 16 is the entire blower, 12 is an outer wall, and two plate-like mouth rings that divide the suction side and the discharge side on the outer periphery of the blade 8, the first mouth ring 10, the second mouth ring The outer periphery of the mouth ring 11 is enclosed. Reference numeral 14 denotes a swirl flow circulation space having an opening 13 facing the blade 8 between the first mouth ring 10 and the second mouth ring 11. Reference numerals 15 a and 15 b denote a plurality of columns provided in the swirl flow circulation space, and are provided so as to extend from the opening edges of the first mouth ring 10 and the second mouth ring 11 in the substantially radial direction of the blade 8.

  With this configuration, when the air blower 16 is installed and the configuration of the product air passage, when the air passage resistance is high as in the refrigerator, the radius passing through the blade 8 as shown in FIG. A part of the airflow G having a large directional velocity component flows into the swirl circulation space 14 through the opening 13.

  Here, as shown in FIG. 19, first, immediately after the blade 8 passes through one column 15a, the air flow H is generated on the side where the blade 8 of the column 15a moves away, and the circumferential direction between the column 15a and the next column 15b. The airflow I flows into the swirling flow circulation space 14 from the pressure surface 5 side of the blade 8 on the side where the airflow I approaches the blade 8 of the next column 15b that the blade 8 approaches. At that time, the rotating blade 8 turns into a swirling flow flowing in the circumferential direction of the blade 8 and flows in the swirling flow circulation space 14.

  Then, as shown in FIG. 20, when the blade 8 moves in the rotational direction and passes through the next column 15b, the airflows H, I, and J are all prevented from turning around the column 15b, and the direction of flow is the blade. It is deflected in eight directions, and is discharged again from the suction surface 7 side of the blade 8 to the blade 8 side.

  As described above, since the velocity of the airflow flowing along the negative pressure surface 7 side is increased by discharging from the swirling flow circulation space 14 to the low pressure portion of the blade 8 on the negative pressure surface 7 side, the pressure surface 5 side Disturbances that occur at the time of merging with the discharge airflow can be more effectively suppressed. In addition, a part of the airflow passing through the impeller is sucked and exhausted in the swirl circulation space 14 and discharged again to the discharge side, thereby suppressing the deterioration of the blowing performance of the impeller and suppressing the increase of blowing noise. Can do.

(Embodiment 4)
FIG. 21 shows a refrigerator-freezer according to Embodiment 4 of the present invention. In addition, the same code | symbol is attached | subjected about the part of the same structure as Embodiment 1 to Embodiment 3, and description is abbreviate | omitted.

  In FIG. 21, reference numeral 150 denotes the entire refrigerator / refrigerator, and 101 denotes a storage room. The air sucked from the storage room air suction port 102 by the blower 16 passes through the air path and is heat-exchanged by the evaporator 103, from the storage room air discharge port 104. Air that is discharged and cooled to the storage chamber 101 is supplied. The blower 16 is used in an air passage that supplies cooling air to the storage chamber 101 in the refrigerator. In the present embodiment, these are configured in an upper stage and a lower stage, respectively.

  A machine room 105 includes a compressor 106, an evaporating dish 107, and a condenser 108. The air sucked from the machine room air suction port 109 by the blower 16 a passes through the air passage, is heat-exchanged by the condenser 108, and is discharged from the machine room air discharge port 110. The blower 16a is used in an air passage that supplies air into the machine room 105 of the refrigerator.

  With this configuration, it is possible to suppress the deterioration of the blowing performance as the blowers 16 and 16a under the condition of high airflow resistance like the refrigerator refrigerator 150.

  Therefore, since the amount of air passing through the evaporator 103 is increased, the efficiency of heat exchange is improved, and the cooling capacity of the refrigerator-freezer 150 is improved. Further, since the amount of air passing through the condenser 108 and the compressor 106 is increased, the compressor 106 can be cooled, the efficiency of heat exchange of the condenser 108 is improved, and the condensing capacity of the refrigerator refrigerator 150 is improved.

Front view of impeller in Embodiment 1 of the present invention Sectional drawing of the aa line of FIG. The principal part front view which shows the effect | action of the impeller in Embodiment 1 of this invention Sectional drawing of the bb line of FIG. 3 which shows the effect | action of the impeller in Embodiment 1 of this invention Sectional drawing of the bb line of FIG. 3 which shows the other effect | action of the impeller in Embodiment 1 of this invention. 3 is a cross-sectional view taken along the line cc of FIG. 3 showing the operation of the impeller in the conventional example. FIG. 3 is a cross-sectional view taken along the line dd in FIG. 3, illustrating the operation of the impeller according to the first embodiment of the present invention. The characteristic view which shows the comparison of the aerodynamic (PQ) characteristic of the air blower in Embodiment 1 of this invention, and the impeller of a prior art example The principal part front view of the other impeller in Embodiment 1 of this invention The principal part front view of the other impeller in Embodiment 1 of this invention The principal part front view of the other impeller in Embodiment 1 of this invention The principal part front view of the impeller in Embodiment 1 of this invention The characteristic view showing the relationship between the center position DM of the convex part and the static pressure P of the operating point in the first embodiment of the present invention The characteristic view showing the relationship between the length DT of the base of the convex part in Embodiment 1 of this invention, and the static pressure P of a driving | running operation point The characteristic view showing the relationship between the height H of the convex part in Embodiment 1 of this invention, and the static pressure P of a driving | running operation point The principal part front view which shows the effect | action of the impeller in Embodiment 2 of this invention Front view of a blower in Embodiment 3 of the present invention Sectional view of line ee in FIG. Sectional drawing of the ff line | wire of FIG. 18 which shows the effect | action of the air blower in Embodiment 3 of this invention. 19 is a cross-sectional view of the blade of FIG. Side surface longitudinal cross-sectional view of the refrigerator-freezer in Embodiment 4 of this invention Front view of impeller in conventional example Sectional drawing of the xx line of FIG. Front view of essential parts showing the operation of the impeller in the conventional example Sectional drawing of the yy line of FIG.

Explanation of symbols

2 Motor 3 Hub 5 Pressure surface 8 Blade 8a Convex part (air flow adhesion means)
8b Concavity (airflow direction changing means)
DESCRIPTION OF SYMBOLS 9 Impeller 10 1st mouth ring 11 2nd mouth ring 12 Outer wall 13 Opening part 14 Swirling flow circulation space 15a, 15b Pillar 16, 16a Blower 101 Storage room 105 Machine room 150 Refrigeration refrigerator

Claims (7)

  A hub attached to the motor, and a plurality of blades provided around the hub, and an airflow direction changing means for converting the airflow sucked into the blades provided on the pressure surface side of the blades into an axial direction. The airflow adhering means for adhering the separated flow provided at the rear edge of the blades in the vicinity where the airflow converted in the axial direction by the airflow direction converting means flows is provided for each of the plurality of blades. Characteristic impeller.   The impeller according to claim 1, wherein the position of the airflow direction changing means extends to the position of the airflow attaching means.   A hub attached to the motor, and a plurality of blades provided around the hub, and an airflow direction changing means for converting the airflow sucked into the blades provided on the pressure surface side of the blades into an axial direction. An impeller having airflow adhering means for adhering a separated flow provided at the rear edge of the blades in the vicinity of the flow of the airflow converted in the axial direction by the airflow direction changing means for each of the plurality of blades And an orifice surrounding the outer periphery of the impeller encloses the outer periphery of the first and second plate-like mouth rings that define the suction side and the discharge side, and the first and second plate-like mouth rings. A swirl flow circulation space having an opening facing the blades of the impeller is provided between the outer wall and the first and second plate-like mouth rings, and the first and second plate-like mouth rings Extending from the opening edge in the substantially radial direction of the impeller Blower, characterized in that there are a plurality of columns provided.   4. A blower according to claim 3, wherein the position of the airflow direction changing means of the impeller extends to the position of the airflow attaching means.   A hub attached to the motor, and a plurality of blades provided around the hub, and an airflow direction changing means for converting the airflow sucked into the blades provided on the pressure surface side of the blades into an axial direction. An impeller having airflow adhering means for adhering a separated flow provided at the rear edge of the blades in the vicinity of the flow of the airflow converted in the axial direction by the airflow direction changing means for each of the plurality of blades And an orifice surrounding the outer periphery of the impeller encloses the outer periphery of the first and second plate-like mouth rings that define the suction side and the discharge side, and the first and second plate-like mouth rings. A swirl flow circulation space having an opening facing the blades of the impeller is provided between the outer wall and the first and second plate-like mouth rings, and the first and second plate-like mouth rings Extending from the opening edge in the substantially radial direction of the impeller Blower, characterized in that there is a plurality of posts provided, refrigerator used for air passage for supplying cooling air to the storage compartment in the refrigerator.   A hub attached to the motor, and a plurality of blades provided around the hub, and an airflow direction changing means for converting the airflow sucked into the blades provided on the pressure surface side of the blades into an axial direction. An impeller having airflow adhering means for adhering a separated flow provided at the rear edge of the blades in the vicinity of the flow of the airflow converted in the axial direction by the airflow direction changing means for each of the plurality of blades And an orifice surrounding the outer periphery of the impeller encloses the outer periphery of the first and second plate-like mouth rings that define the suction side and the discharge side, and the first and second plate-like mouth rings. A swirl flow circulation space having an opening facing the blades of the impeller is provided between the outer wall and the first and second plate-like mouth rings, and the first and second plate-like mouth rings Extending from the opening edge in the substantially radial direction of the impeller Blower, characterized in that there is a plurality of posts provided, refrigerator used for air passage for supplying air to the refrigerator of the machine room.   The refrigerator according to claim 5 or 6, wherein the position of the airflow direction changing means of the impeller in the blower extends to the position of the airflow attaching means.

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